Air conditioning system with multiple-effect evaporative condenser

ABSTRACT

An air conditioning system includes a multiple effect evaporative condenser, at least one compressor, at least one heat exchanger, an expansion valve, and at least one multiple-effect evaporative condensers. The multiple effect evaporative condenser and the heat exchanger utilize a highly efficient heat exchanging pipe for performing heat exchange between water and refrigerant.

CROSS REFERENCES TO RELATED APPLICATIONS

This is a divisional application of a non-provisional application havingan application number of Ser. No. 13/506,462 and a filing date of Apr.21, 2012. The contents of this specifications, including any interveningamendments thereto, are incorporated herein by reference.

BACKGROUND OF THE PRESENT INVENTION

Field of Invention

The present invention relates to an air conditioning system, and moreparticularly to an air conditioning system utilizing a multiple effectevaporative condenser for effectively and efficiently coolingrefrigerant.

Description of Related Arts

Referring to FIG. 1 to FIG. 2 of the drawings, a conventional condenser1002P and a conventional cooling tower 1001P for a central airconditioning system is illustrated. The conventional cooling tower 1001Pand the conventional condenser 1002P are connected through water pipes931P, 923P in which cooling water 924P is pumped by a pumping device932P to circulate between the cooling tower 1001P and the condenser 1002through the water pipes 931P, 923P. The cooling tower 1001P is usuallyinstalled on an exterior of a building, such as on the roof of thebuilding.

Vaporous refrigerant (coming from a compressor of the central airconditioning system) having an elevated temperature enters the condenser1002P and is arranged to perform heat exchange with the cooling water924P coming from the cooling tower 1001P. After the heat exchangeprocess, the vaporous refrigerant will be cooled down and transformedinto liquid state. The liquid refrigerant 935P is arranged to leave thecondenser 1002P and go back to the evaporator for another compressioncycle.

The cooling water 924P circulates between the cooling tower 1001P andthe condenser 1002P. While in the condenser 1002P, the cooling water924P absorbs heat from the vaporous refrigerant and the temperature ofthe cooling water 924P thereby increases. After absorbing heat, thecooling water 924P is pumped backed to the cooling tower 1001P throughthe water pipe 923P for being cooled down by the cooling tower 1001P.The cooling water 924P having a lower temperature then circulates backto the condenser 1002P through the water pipe 931P for another cycle ofheat exchange with the vaporous refrigerant. Conventionally, thetemperature of the cooling water 924P leaving the cooling tower 1001P isapproximately 32° C., while the temperature of the cooling water 924Pleaving the condenser 1002P (i.e. after absorbing heat from the vaporousrefrigerant) is approximately 37° C.

The cooling water 924P leaving the condenser 1002P is collected at a topwater collection basin 925P. The cooling tower 1001P comprises a towerhousing having a receiving cavity, an air inlet 929P and an air outlet930P both communicated with the receiving cavity, wherein the top watercollection basin 925P is provided on top of the tower housing. Thecooling tower 1001P further comprises a bottom water collection basin928P, and a predetermined amount of fill material 926P received in thereceiving cavity. The cooling water 924P collected in the top watercollection basin 925P is guided (by gravity) to flow into the receivingcavity and in physical contact with the fill material 926P to form awater film. Ambient air is sucked into the receiving cavity through theair inlet 929P and is arranged to perform heat exchange with the coolingwater 924P passing through the fill material 926P. After the heatexchange, the air is arranged to exit the cooling tower 1001 through theair outlet 929P while the cooling water 924P is collected at the bottomwater collection basin 928P, which is connected to the condenser 1002P.

There exist a number of disadvantages in association with theabove-mentioned air conditioning system. First, for the condenser 1002Pas described above, the lower the temperature for the cooling water 924Pcoming into the condenser 1002P, the better the performance of coolingthe vaporous refrigerant, and the lower the temperature of the coolingwater 924P coming out of the condenser 1002P. For the cooling tower1001P, however, the higher the temperature of the cooling water 924Pcollected in the top water collection basin 925P, the more effective theheat exchange between the air and the cooling water 924P flowing throughthe fill material 926P. In other words, there is a relative relationshipbetween the temperature requirement of the cooling water 924P of thecondenser 1002P and the cooling tower 1001P.

Second, referring to FIG. 2 of the drawings, the cooling tower 1001P isfilled with the fill material 926P for guiding the water film to performheat exchange with ambient air flowing through the fill material 926P.Water flowing into the top water collection basin 925P is guided to flowthrough the fill material (in the form of a thin water film) along alongitudinal direction of the water tower 1001P. Yet from a practicalperspective, there is a gradual increase of air temperature between theair inlet 929P and the air outlet 930P because air is drawn from the airinlet 929P to the air outlet 930P. On the other hand, there exists agradual decrease in heat exchange performance along a transversedirection of the cooling tower 1001P. As shown in FIG. 2 of thedrawings, if the cooling tower 1001P is hypothetically divided into foursections, namely W₁, W₂, W₃, and W₄, the heat exchange performance inthese four sections are different because of their differing airtemperature. As a result, the cooling water 924P coming out from thesefour sections are of differing temperature, yet they are all collectedat the bottom water collection basin 928P. Hence, the overalltemperature of the cooling water 924P leaving the cooling tower 1001Pthrough the water pipe 931P is actually the resulting temperature of thecooling water 924P after mixing from the four different sections of thefill material 926P (as shown in FIG. 1).

Third, as shown in FIG. 1, the conventional cooling tower airconditioning system requires the use of very long pipes (such as thewater pipes 923P, 931P) for connecting the various components thereof.For example, when the air conditioning system and the cooling tower1001P are installed in different locations, the length of the pipeswhich connect the cooling tower 1001P and the condenser 1002P must bevery long, such that the cooling tower 1001P is typically located at theroof of the building while the condenser 1002P is located somewherewithin the building. Such an extensive piping system requires cumbersomemaintenance procedures and constitutes substantial waste of rawmaterials. Moreover, since the ducts connecting the cooling tower 1001Pand the condenser 1002P are very long in length, very great resistancewill be developed within the ducts so that the energy needed to pump thecooling water circulating between the cooling tower 1001P and thecondenser 1002P is necessarily wasted. This substantially reduces theefficiency of the entire cooling tower air conditioning system.

SUMMARY OF THE PRESENT INVENTION

The invention is advantageous in that it provides a multiple-effectevaporative condenser, wherein heat exchange within the multiple-effectevaporative condenser is optimally carried out for facilitatingeffective and efficient rejection of heat from the refrigerant.

Another advantage of the invention is to provide a multiple-effectevaporative condenser, which eliminates the need to have many andextensive piping and components between conventional cooling towers andcondensers for conventional central air conditioning systems.

Another advantage of the invention is to provide a multiple-effectevaporative condenser which utilizes a plurality of highly efficientheat exchanging pipes providing a relatively large area of heatingexchanging surfaces for performing heat exchange between cooling waterand refrigerant.

Another advantage of the invention is to provide a multiple-effectevaporative condenser which comprises a plurality of heat exchangingunits adapted for performing heat exchange between ambient air, cooingwater and refrigerant in a multi-staged manner (i.e. in temperaturegradients), so as to resolve the inconsistent and unsatisfactory heatexchange problems in conventional cooling towers mentioned above.

Another advantage of the invention is to a provide a multiple-effectevaporative condenser which is capable of increasing saturated airtemperature at the air outlet so as to enhance the heat exchangeperformance of the multiple-effect evaporative condenser.

Another advantage of the invention is to provide a heat exchanger, whichis capable of efficiently facilitating heat exchange between refrigerantand water by using highly efficient heat exchanging pipe.

Another advantage of the invention is to provide a highly efficient heatexchanging pipe which comprises a plurality of inner heat exchangingfins providing relatively large contact surface area and a plurality ofouter heat exchanging fins for forming large heat exchanging surfacearea. More specifically, the highly efficient heat exchanging pipe iscapable of achieving critical heat flux density for a given material ofthe highly efficient heat exchanging pipe.

Additional advantages and features of the invention will become apparentfrom the description which follows, and may be realized by means of theinstrumentalities and combinations particular point out in the appendedclaims.

According to the present invention, the foregoing and other objects andadvantages are attained by providing a multiple-effect evaporativecondenser for cooling a predetermined amount of refrigerant by apredetermined amount of cooling water, comprising: a pumping deviceadapted for pumping said cooling water at a predetermined flow rate; atower housing having an air inlet and an air outlet, wherein an airdraft is drawn between said air inlet and said air outlet; a first watercollection basin mounted in said tower housing for collecting saidcooling water pumped from said pumping device; a first cooling unitcomprising a plurality of heat exchanging pipes and a first fillmaterial unit provided underneath said heat exchanging pipes, whereinsaid cooling water collected in said first water collection basin isarranged to flow through exterior surfaces of said heat exchanging pipesand said first fill material unit; and a bottom water collection basinpositioned underneath said first cooling unit for collecting saidcooling water flowing from said first cooling unit, wherein said coolingwater collected in said bottom water collection basin is arranged to bepumped back to said first water collection basin by said pumping device,wherein said refrigerant flows through said heat exchanging pipes ofsaid first cooling unit, in such a manner that said refrigerant isarranged to perform highly efficient heat exchanging process with saidcooling water for lowering a temperature of said refrigerant, whereinsaid predetermined amount of air is drawn into said tower housingthrough said air inlet for performing heat exchange with said coolingwater flowing through said first fill material for lowering atemperature of said cooling water, wherein said air having absorbed saidheat from said cooling water is discharged out of said tower housingthrough said air outlet.

In accordance with another aspect of the invention, the presentinvention provides a high efficiency heat exchanging pipe, comprising: apipe body; a plurality of inner heat exchanging fins, capable of havingvarious shapes, spacedly and protrudedly extended along an inner surfaceof the pipe body in a spiral manner for enhancing heat exchange surfacearea of the corresponding heat exchanging pipe, and for guiding a fluidflow on the inner surface of the corresponding heat exchange pipe alongthe spiral path of the inner heat exchanging fins; and a plurality ofouter heat exchanging fins, capable of having various shapes, spacedlyand protrudedly extended along an outer surface of the pipe body forenhancing heat exchange surface area of the corresponding heatexchanging pipe and for guiding a fluid flow on the outer surface of thecorresponding heat exchange pipe along the outer heat exchanging fins.

In accordance with another aspect of the invention, the presentinvention provides a heat exchanger, comprising: a heat exchangerhousing having a water inlet, a water outlet, a refrigerant inlet, arefrigerant outlet, and a cover detachably provided on the heatexchanger housing; an upper water chamber provided on an upper portionof the heat exchanger housing, and is communicated with the wateroutlet; a lower water chamber provided on a lower portion of the heatexchanger housing, and is communicated with the water inlet; and atleast one heat exchanging pipes extended between the upper water chamberand the lower water chamber, wherein water having a relatively lowtemperature is arranged to enter the heat exchanger through the waterinlet and temporarily store in the lower water chamber, wherein thewater is pumped up the heat exchanger housing through the heatexchanging pipes and temporarily stored in the upper water chamber, andleaves the heat exchanger through the water outlet, wherein the heatexchanging pipe comprises a pipe body, a plurality of inner heatexchanging fins inwardly extended from the pipe body, and a plurality ofouter heat exchanging fins outwardly extended from the pipe body,wherein the refrigerant is guided to enter the heat exchanger throughthe refrigerant inlet and flow through an exterior of outer heatexchanging fins of the heat exchanging pipes for performing heatexchange with the water flowing through the corresponding inner heatexchanging fins of the heat exchanging pipes, wherein heat is absorbedby the refrigerant which becomes evaporated, wherein vapor of therefrigerant is then guided to leave the heat exchanger through therefrigerant outlet.

Still further objects and advantages will become apparent from aconsideration of the ensuing description and drawings. These and otherobjectives, features, and advantages of the present invention willbecome apparent from the following detailed description, theaccompanying drawings, and the appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram of a conventional cooling tower and aconventional condenser of a central air conditioning system.

FIG. 2 is a schematic diagram of a cooling tower of the conventional airconditioning system.

FIG. 3 is a perspective view of a multiple-effect evaporative condenseraccording to a preferred embodiment of the present invention.

FIG. 4 is a schematic diagram of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention.

FIG. 5 is a schematic diagram of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating the flow path of the refrigerant.

FIG. 6 is a schematic diagram of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating one of the cooling units and the heat exchangingpipes.

FIG. 7 is another schematic diagram of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating that the first water collection basin isequipped with a basin partitioning plate.

FIG. 8 is a first alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating that the multiple-effect evaporative condenseris part of a central air conditioning system.

FIG. 9 is a first alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating a sectional side view of the multiple-effectevaporative condenser shown in FIG. 8.

FIG. 10 is a first alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating that the multiple-effect evaporative condenserhas first through third cooling unit.

FIG. 11 is a zoom-in diagram of the multiple-effect evaporativecondenser according to the first alternative mode of the above preferredembodiment of the present invention.

FIG. 12 is a side view of the multiple-effect evaporative condenseraccording to the first alternative mode of the above preferredembodiment of the present invention, illustrating the side view of theheat exchanging pipes shown in FIG. 10 and FIG. 11.

FIG. 13 is a plan sectional view of the multiple-effect evaporativecondenser according to the first alternative mode of the above preferredembodiment of the present invention, illustrating the heat exchangingpipes as shown from the top of the multiple-effect evaporative condenserdepicted in FIG. 10 and FIG. 11 along the plane 13-13.

FIG. 14 is a first alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating that the multiple-effect evaporative condenserhas only one cooling unit.

FIG. 15A to FIG. 15C are schematic diagrams of a second alternative modeof the multiple-effect evaporative condenser according to the abovepreferred embodiment of the present invention.

FIG. 16 is a third alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention.

FIG. 17A to FIG. 17C are schematic diagrams of a third alternative modeof the multiple-effect evaporative condenser according to the abovepreferred embodiment of the present invention, illustrating the heatexchanging pipes and the flow of the refrigerant.

FIG. 18A to FIG. 18C are schematic diagrams of a third alternative modeof the multiple-effect evaporative condenser according to the abovepreferred embodiment of the present invention.

FIG. 19 is a fourth alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention.

FIG. 20 is a fourth alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating the flow path of the refrigerant in the firstcooling unit.

FIG. 21 is a fourth alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating the flow path of the refrigerant the secondcooling unit.

FIG. 22 is a fifth alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention.

FIG. 23 is a fifth alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating the flow path of the refrigerant in the firstcooling unit.

FIG. 24 is a fifth alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating the flow path of the refrigerant in the secondcooling unit.

FIG. 25 is a fifth alternative mode of the multiple-effect evaporativecondenser according to the above preferred embodiment of the presentinvention, illustrating the flow path of the refrigerant in the thirdcooling unit.

FIG. 26A to FIG. 26C are schematic diagrams of a sixth alternative modeof the multiple-effect evaporative condenser according to the abovepreferred embodiment of the present invention.

FIG. 27 is a plan view of the multiple-effect evaporative condenseraccording to the sixth alternative mode of the above preferredembodiment of the present invention.

FIG. 28A to FIG. 28C schematic diagrams of the multiple-effectevaporative condenser according to the sixth alternative mode of theabove preferred embodiment of the present invention, illustrating theflow path of the refrigerant.

FIG. 29 is a perspective view of a heat exchanging pipe according to theabove preferred embodiment of the present invention.

FIG. 30 is a side view of the heat exchanging pipe according to theabove preferred embodiment of the present invention.

FIG. 31 is a sectional side view of the heat exchanging pipe accordingto the above preferred embodiment of the present invention, illustratingthe sectional side view alone plane 2-2 of FIG. 30.

FIG. 32 is a sectional top view of the heat exchanging pipe according tothe above preferred embodiment of the present invention, illustratingthe sectional side view alone plane 3-3 of FIG. 30.

FIG. 33 is a sectional top view of the heat exchanging pipe according tothe above preferred embodiment of the present invention, illustratingthe inner heat exchanging fins and the outer heat exchanging fins have“I” cross sectional shape.

FIG. 34A to 34I illustrate the different cross sectional shapes of theheat exchanging fins according to the above preferred embodiment of thepresent invention.

FIG. 35A and FIG. 35B are schematic diagrams of the heat exchanging pipeaccording to the above preferred embodiment of the present invention,illustrating that the heat exchanging pipe can be used in conjunctionwith an outer protective pipe.

FIG. 36 is a schematic diagram of the first alternative mode of the heatexchanging pipe according to the above preferred embodiment of thepresent invention, illustrating that the heat exchanging pipe isembedded by the outer protective pipe.

FIG. 37 is a perspective view of an alternative mode of the heatexchanging pipe according to the above preferred embodiment of thepresent invention.

FIG. 38 is a sectional front view of the alternative mode of the heatexchanging pipe according to the above preferred embodiment of thepresent invention.

FIG. 39 is a side view of the alternative mode of the heat exchangingpipe according to the above preferred embodiment of the presentinvention.

FIG. 40 is a side view of the alternative mode of the heat exchangingpipe according to the above preferred embodiment of the presentinvention, illustrating that the outer heat exchanging fin has acircular cross section.

FIG. 41 is a side view of a heat exchanger according to the abovepreferred embodiment of the present invention.

FIG. 42 is a sectional side view of a heat exchanger according to theabove preferred embodiment of the present invention, wherein thesectional side view is made alone plane 10-10 of FIG. 41.

FIG. 43 is a sectional plan view of the heat exchanger according to theabove preferred embodiment of the present invention, wherein thesectional side view is made alone plane 11-11 of FIG. 42.

FIG. 44 is a partial schematic diagram the heat exchanger according tothe above preferred embodiment of the present invention.

FIG. 45 is a first alternative mode of the heat exchanger according tothe above preferred embodiment of the present invention.

FIG. 46 is a sectional side view of the first alternative mode of theheat exchanger according to the above preferred embodiment of thepresent invention.

FIG. 47 is a second alternative mode of the heat exchanger according tothe above preferred embodiment of the present invention.

FIG. 48 is a sectional side view of the second alternative mode of theheat exchanger according to the above preferred embodiment of thepresent invention.

FIG. 49 is a sectional side view (along plane 17-17 of FIG. 47) of thesecond alternative mode of the heat exchanger according to the abovepreferred embodiment of the present invention.

FIG. 50 is a sectional side view (along plane 18-18 of FIG. 49) of thesecond alternative mode of the heat exchanger according to the abovepreferred embodiment of the present invention.

FIG. 51 is a third alternative mode of the heat exchanger according tothe above preferred embodiment of the present invention.

FIG. 52 is a sectional side view (along plane 20-20 of FIG. 51) of thethird alternative mode of the heat exchanger according to the abovepreferred embodiment of the present invention.

FIG. 53 is a partial zoom-in schematic diagram of the third alternativemode of the heat exchanger according to the above preferred embodimentof the present invention, illustrating the upper portion of the heatexchanger housing.

FIG. 54 is a sectional plan view of the third alternative mode of theheat exchanger according to the above preferred embodiment of thepresent invention.

FIG. 55A to FIG. 55F are schematic diagrams of an additional coolingdevice according to the above preferred embodiment of the presentinvention.

FIG. 56 is schematic diagram of two of the heat exchangers according tothe above preferred embodiment of the present invention, illustratingthat the two heat exchangers are connected in a side-by-side manner.

FIG. 57 is schematic diagram of two of the heat exchangers according tothe above preferred embodiment of the present invention, illustratingthat the two heat exchangers are connected in a series manner.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring to Referring to FIG. 3 to FIG. 6 of the drawings, amultiple-effect evaporative condenser 100 for an air conditioning systemaccording to a preferred embodiment of the present invention isillustrated. The air conditioning system is for cooling a predeterminedspace, such as a particular space within a building, by using apredetermined amount of cooling water 1 and refrigerant 3 (as shown inFIG. 8). The components of the air conditioning system will be discussedone by one below. However, it is worth noting that some of thecomponents are by themselves patentably distinctive and may be used inapplications other than air conditioning systems.

The multiple-effect evaporative condenser 100 comprises a pumping device10 adapted for pumping the cooling water 1 at a predetermined flow rate,a tower housing 200 having an air inlet 201 and an air outlet 202,wherein an air draft is drawn between the air inlet 201 and the airoutlet 202.

The multiple-effect evaporative condenser 100 further comprises a firstwater collection basin 21 mounted in the tower housing 200 forcollecting the cooling water 1 pumped from the pumping device 10.

The multiple-effect evaporative condenser 100 further comprises a firstcooling unit 24 comprising a plurality of heat exchanging pipes 241-244and a first fill material unit 245 provided underneath the heatexchanging pipes 241-244, wherein the cooling water 1 collected in thefirst water collection basin 21 is arranged to flow through exteriorsurfaces of the heat exchanging pipes 241-244 and then through the firstfill material unit 245.

The multiple-effect evaporative condenser 100 further comprises a secondwater collection basin 22 positioned underneath the first cooling unit24 for collecting the cooling water 1 flowing from the first coolingunit 24, wherein the cooling water 1 collected in the second watercollection basin 22 is arranged to be pumped back to the first watercollection basin 21 by the pumping device 10, wherein the refrigerant 3flows through the heat exchanging pipes 241-244 of the first coolingunit 24 in such a manner that the refrigerant 3 is arranged to flowthrough at least one heat exchanging route for perform highly efficientheat exchanging process with the cooling water 1 for lowering atemperature of the refrigerant 3, wherein the predetermined amount ofair is drawn into the tower housing 200 through the air inlet 201 forperforming heat exchange with the cooling water 1 flowing through thefirst fill material unit 245 for lowering a temperature of the coolingwater 1, wherein the air having absorbed the heat from the cooling water1 is discharged out of the tower housing 200 through the air outlet 202.

According to the preferred embodiment of the present invention, themultiple-effect evaporative condenser 100 further comprises a secondcooling unit 25 provided underneath the second water collection basin 22for allowing the cooling water to undergo a second cycle of heating bythe refrigerant and cooling by flowing through a second fill materialunit 255.

The second water collection basin 22 is arranged for collecting thecooling water 1 flowing from the first cooling unit 24. The secondcooling unit 25 comprises a plurality of heat exchanging pipes 251-254,and a predetermined amount of second fill material unit 255, wherein thecooling water 1 collected in the second water collection basin 22 isarranged to flow through exterior surfaces of the heat exchanging pipes251-254 of the second cooling unit 25 and the second fill material unit255.

The refrigerant 3 is arranged to follow at least one heat exchangingroute formed by the heat exchanging pipes 241-244 of the first coolingunit 24 and the second cooling unit 25.

In this preferred embodiment, the multiple-effect evaporative condenser100 further comprises a third water collection basin 23 positionedunderneath the second cooling unit 25 for collecting the cooling water 1flowing from the second cooling unit 25, wherein the cooling water 1collected in the third water collection basin 23 is arranged to bepumped back to the first water collection basin 21 by the pumping device10, wherein the refrigerant 3 flows through the heat exchanging pipes241-244 in such a manner and flow sequent that the refrigerant 3 isarranged to perform heat exchange with the cooling water 1 flowingthrough the multiple-effect evaporative condenser 100 for lowering atemperature of the refrigerant 3, wherein the predetermined amount ofair is sucked into the tower housing 200 through the air inlet 201 forperforming heat exchange with the cooling water 1 flowing through thefirst cooling unit 24 and the second cooling unit 25 for lowering atemperature of the cooling water 1, wherein the air having absorbed theheat from the cooling water 1 is discharged out of the multiple-effectevaporative condenser 100 through the air outlet 202.

It is important to mention at this stage that the multiple-effectevaporative 10 condenser 100 is “multiple-layer” and“multiple-effective” in the sense that when the cooling water 1 isundergoing multiple heat exchange processes between the cooling waterand the refrigerant. Every time the cooling water 1 passes through thecooling unit 24 (25), it is heated up by the refrigerant andsubsequently cooled down by flowing through the corresponding fillmaterial unit 245 (255). Thus, take FIG. 4 as an example, the coolingwater 1 is arranged to pass through the first cooling unit 24 to undergoa heat exchange process between the cooling water 1 and the refrigerantfor once (the cooling water 1 is heated up by the refrigerant and thencooled down by flowing through the first fill material unit 245), andthen to flow to the second cooling unit 25 for undergoing another heatexchange process between the cooling water 1 and the refrigerant (thecooling water 1 is heated up by the refrigerant and then cooled down byflowing through the second fill material unit 255 once again). In otherwords, one unit of cooling water 1 will be utilized for at least onetime for each cycle of heating and cooling processing.

After the cooling water 1 has passed through the first cooling unit 24and the second cooling unit 25, the pumping device 10 is provided in thetower housing 200 and 25 is arranged pump the cooling water 1 from thethird water collection basin 23 up to the first water collection basin21. In this preferred embodiment, a vertical distance (i.e. height)between the first water collection basin 21 and the third watercollection basin 23 is embodied as generally not more than 4.5 m. Onlywhen the multiple-effect evaporative condenser comprises three coolingunits that the overall height of it exceeds 4.5 m.

There exists a plurality of heat exchanging pipes 241-244 extendingbetween the first cooling unit 24 and the second cooling unit 25. Theexact number of heat exchanging pipes 241-244, 251-255 and the manner inwhich the refrigerant 3 circulates is determined by the applicationcircumstances of the present invention and the number of cooling unitsin the multiple-effect evaporative condenser 100.

The first water collection basin 21 has a first bottom tank panel 211, afirst side tank panel 212, a plurality of through first passage holes213 formed on the bottom tank panel 211, wherein the cooling water 1 isarranged to be pumped into the first water collection basin 21 by thepumping device 10 and reaches the first cooling unit 24 through thefirst passage holes 213. More specifically, the first cooling unit 24further comprises a first supporting tray 246 having a first traypartition member 2463 upwardly extended from a bottom surface thereoffor dividing the first supporting tray 246 into a first tray section2461 and a second tray section 2462. According to the present preferredembodiment, it is embodied to have two of the first heat exchangingpipes 241, 242 (i.e. the first the first heat exchanging pipe 241 andthe second heat exchanging pipe 242) spacedly supported in the firsttray section 2461 and another two of the heat exchanging pipes 243, 244(i.e. the third heat exchanging pipe 243 and the fourth heat exchangingpipe 244) spacedly supported in the second tray section 2462.

Furthermore, the first water collection basin 21 further has a pluralityof first dividers 214 spacedly and downwardly extended from the bottomtank panel 211 to define a plurality of first trapping cavities 215between each two corresponding adjacent first dividers 214, wherein eachof the first through fourth heat exchanging pipes 241, 242, 243, 244 aresupported within each of the first trapping cavities 215 respectively sothat when the cooling water 1 falls into the first trapping cavities 215through the corresponding first passage hole 213, the cooling water 1 isguided to substantially embed the corresponding heat exchanging pipes240 for ensuring efficient and effective heat exchange between the heatexchanging pipes 240 and the cooling water 1.

The first supporting tray 246 further has a plurality of first throughpassing holes 2467 formed thereon wherein the cooling water 1 collectedat the first supporting tray 246 is allowed to flow into the first fillmaterial unit 245.

The first fill material unit 245 comprises a first fill material pack2451 and a second fill material pack 2452 spacedly supported in thetower housing 200, wherein the cooling water 1 coming from the firsttray section 2461 is arranged to drop into the first fill material pack2451, while the cooling water 1 coming from the second tray section 2462is arranged to drop into the second fill material pack 2452. Asmentioned below, since the temperature of the refrigerant 3 flowingthrough the first heat exchanging pipe 241 and the second heatexchanging pipe 242 is different from that of the refrigerant 3 flowingthrough the third heat exchanging pipe 243 and the fourth heatexchanging pipe 244, the temperature of the cooling water 1 entering thefirst fill material pack 2451 and the temperature of the cooling water 1entering the second fill material pack 2452 are also different. This hasa substantial difference in heat exchange performance in the first fillmaterial pack 2451 and the second fill material pack 2452.

On the other hand, the second water collection basin 22 has a secondbottom tank panel 221, a second side tank panel 222, a plurality ofsecond passage holes 223 formed on the second bottom tank panel 221,wherein the cooling water 1 dripping from the first fill material unit245 is arranged to be collected at the second water collection basin 22and reaches the second cooling unit 25 through the second passage holes223.

Referring to FIG. 4 and FIG. 6 of the drawings, the second watercollection basin 22 further comprises a separation member 226 upwardlyextended from the second bottom tank panel 221 to separate the secondwater collection basin 22 into a first collection chamber 227 and asecond collection chamber 228, wherein the cooling water 1 coming fromthe first fill material pack 2451 is collected at the first collectionchamber 227, while the cooling water 1 coming from the second fillmaterial pack 2452 is collected at the second collection chamber 228.

A shown in FIGS. 4 and 6, the second cooling unit 25 further comprises asecond supporting tray 256 having a second tray partition member 2563upwardly extended from a bottom surface thereof for dividing the secondsupporting tray 256 into a third tray section 2561 and a fourth traysection 2562, wherein two of the heat exchanging pipes 251, 252 (i.e.the fifth heat exchanging pipes 251 and the sixth heat exchanging pipe252) are spacedly supported in the third tray section 2561 and two ofthe heat exchanging pipes 253,254 (i.e. the seventh heat exchanging pipe253 and the eighth heat exchanging pipe 254) are spacedly supported inthe fourth tray section 2562.

Furthermore, the second water collection basin 22 further has aplurality of second dividers 224 spacedly and downwardly extended fromthe second bottom tank panel 221 to define a corresponding number ofsecond trapping cavities 225 between each two corresponding seconddividers 224. According to the present preferred embodiment, there arefour heat exchanging pipes 251, 252, 253, 254 supported within the foursecond trapping cavities 225 respectively so that when the cooling water1 falls into the second trapping cavities 225 through the correspondingsecond passage holes 223, the cooling water 1 is guided to substantiallyembed the corresponding fifth through eighth heat exchanging pipes 251,252, 253, 254 for ensuring efficient and effective heat exchange betweenthe fifth through eighth heat exchanging pipes 251, 252, 253, 254 andthe cooling water 1.

The second supporting tray 256 further has a plurality of second throughpassing holes 2567 formed therein wherein the cooling water 1 collectedat the second supporting tray 256 is allowed to flow into the secondfill material unit 255.

The second fill material unit 255 comprises a third fill material pack2551 and a fourth fill material pack 2552 spacedly supported in thetower housing 200, wherein the cooling water 1 coming from the firsttray section 2561 is arranged to drop into the third fill material pack2551, while the cooling water 1 coming from the second lower traysection 2562 is arranged to drop into the fourth fill material pack2552. Again, since the temperature of the refrigerant 3 flowing throughthe fifth heat exchanging pipe 251 and the sixth heat exchanging pipe252 is different from that of the refrigerant 3 flowing through theseventh heat exchanging pipe 253 and the eighth heat exchanging pipe254, the temperature of the cooling water 1 entering the third fillmaterial pack 2551 and the temperature of the cooling water 1 enteringthe fourth fill material pack 2552 are also different. Finally, thecooling water 1 is collected at the third water collection basin 23 andis pumped back to the first water collection basin 21 for another cycleof heat exchange.

Note that the air is arranged to pass through the first fill materialunit 245 and the second fill material unit 255 for transferring the heatfrom the cooling water 1 through conductive heat transfer. Thus, thecooling water 1 absorbs heat from the refrigerant 3, while the heatabsorbed is then carried away by the air flowing through themultiple-effect evaporative condenser 100.

It is worth mentioning that one of the objects of the present inventionis to enhance a heat transfer performance of the multiple-effectevaporative condenser 100 and to save energy, and one of the methods toachieve this is to increase the saturated air temperature at the airoutlet 202. However, this cannot be accompanied by conventionalevaporative condenser 100 because of the problems mentioned in the“Background” section above. However, one skilled in the art wouldappreciate that the multi-effect evaporative condenser 100 is capable ofaccomplishing multi heat exchange procedures between the cooling water1, the refrigerant 3, and the heat exchanging pipes 241-244 and 251-254.

More specifically, according to the present preferred embodiment, thecooling water 1 has performed two heat exchange cycles when goingthrough from the first water collection basin 21 to the third watercollection basin 23. The cooling water 1 perform heat exchange with therefrigerant 3 first (thereby increasing its temperature) and then withthe incoming air every time it passes through the relevant cooling unit24 (25) (thereby decreasing its temperature). At the same time, therefrigerant 3 performs heat exchange with the cooling water 1 throughthe corresponding heat exchanging pipes 241-244 and 251-254 and heat isextracted to the cooling water 1 which is then cooled by the air flowingbetween the air inlet 201 and the air outlet 202.

Referring to FIG. 3 to FIG. 6 of the drawings, the refrigerant 3entering the multiple-effect evaporative condenser 100 is first guidedto flow through the third heat exchanging pipe 243, the fourth heatexchanging pipe 244, the seventh heat exchanging pipe 253 and the eighthheat exchanging pipe 254. After passing through these heat exchangingpipes 243, 244, 253, 254, the refrigerant 3 is cooled down by a firsttemperature gradient. The refrigerant 3 is then guided to flow throughthe first heat exchanging pipe 241 and the second heat exchanging pipe242, and is further cooled down by a second temperature gradient. Therefrigerant 3 is then guided to flow through the fifth heat exchangingpipe 251 and the sixth heat exchanging pipe 252, and thus is furthercooled down by a third temperature gradient.

Referring to FIG. 7 of the drawings, a first alternative mode of themultiple effect evaporative condenser 100 of the present invention isillustrated, in which the multiple-effect evaporative condenser 100further comprises a second pumping device 10A, and a plurality of basinpartitioning plates 27 provided on the first water collection basin 21and the third water collection basin 23. The basin partitioning plate 27provided on the first water collection basin 21 divides the first watercollection basin 21 into a first water collection compartment 216 and asecond water collection compartment 217. Similarly, the basinpartitioning plate 27 provided on the first water collection basin 23divides the third water collection basin 23 into a third watercollection compartment 231 and a fourth water collection compartment232. The cooling water 1 coming from the third fill material pack 2551and the fourth fill material pack 2552 are separately collected at thethird water collection compartment 231 and the fourth water collectioncompartment 232 and are separately pumped (by the pumping devices 10) tothe first water collection compartment 216 and the second watercollection compartment 217 of the first water collection basin 21respectively.

The purpose of the basin partitioning plates 27 is to preventsubstantial heat transfer of the cooling water 1 in the first watercollection basin 21 and the third water collection basin 23 so as tominimize interference of heat exchange performance at each side of themultiple-effect evaporative condenser 100.

Referring to FIG. 8 of the drawings, a central air conditioning systemis illustrated, in which the central air conditioning system comprises afirst alternative mode of the multiple-effect evaporative condenser 100described above. FIG. 8 illustrates that the multiple-effect evaporatorcondenser 100′ in its first alternative mode (or in its preferredembodiment as described above) may be used in the central airconditioning system. Thus, the central air conditioning system as shownin FIG. 8 comprises a plurality of compressors 40, a plurality of heatexchangers 30 connected to the compressors 40 through a plurality ofexpansion valves 50 respectively, and a plurality of the multiple-effectevaporative condensers 100′ connected to the compressors 40 so thatrefrigerant 3 is guided and pumped to flow through the heat exchangingpipes 241-244 and 251-254. The two multiple-effect evaporativecondensers 100′ are served by one single water pump 10′.

Moreover, the refrigerant 3 is circulated between the multiple-effectevaporative condensers 100′ and the heat exchanger 30 through aplurality of expansion valves 50. The refrigerant 3 in its vaporousstate is compressed to enter the multiple-effect evaporative condensers100′ for heat exchange with the cooling water 1. After heat exchangewith the cooling water 1, the refrigerant is converted into liquid stateand is guided to leave the multiple-effect evaporative condensers 100′and enter the heat exchanger 30. In the heat exchanger 30, therefrigerant 3 absorbs heat and becomes saturated vapor (i.e. vaporousstate). The refrigerant 3 is then compressed to flow back to themultiple-effect evaporative condensers 100′ for another cycle of heatexchange with the cooling water 1.

Referring to FIG. 9 of the drawings, which is a sectional view of themultiple-effect evaporative condensers 100′ served by one pumping device10′ for pumping the cooling water 1 circulating in the multiple-effectevaporative condensers 100′. For each of the multiple-effect evaporativecondensers 100′, the pumping device 10′ is communicated between thethird water collection basin 23′ and the corresponding first watercollection basin 21′.

For each of the multiple-effect evaporative condensers 100′, the firstwater collection basin 21′ has a first bottom tank panel 211′, a firstside tank panel 212′, a plurality of through first passage holes 213′formed on the bottom tank panel 211′, wherein the cooling water 1 isarranged to be pumped into the first water collection basin 21′ andreach the first cooling unit 24′ through the first passage holes 213′.The first cooling unit 24′ comprises a first supporting tray 246′ havinga tray partition member 2463′ upwardly extended from a bottom surfacethereof for dividing the first supporting tray 246′ into a first traysection 2461′ and a second tray section 2462′, wherein two of the heatexchanging pipes 241′, 242′ (i.e. the first heat exchanging pipe 241′and the second heat exchanging pipe 242′) are spacedly supported in thefirst tray section 2461′ and two of the heat exchanging pipes 243′, 244′(i.e. the third heat exchanging pipe 243′ and the fourth heat exchangingpipe 244′) are spacedly supported in the second tray section 2462′.

The first fill material unit 245′ comprises a first fill material pack2451′ and a second fill material pack 2452′ spacedly supported in thetower housing 200′, wherein the cooling water 1 coming from the firsttray section 2461′ is arranged to drop into the first fill material pack2451′, while the cooling water 1 coming from the second tray section2462′ is arranged to drop into the second fill material pack 2452′.

On the other hand, the second water collection basin 22′ has a secondbottom tank panel 221′, a second side tank panel 222′, a plurality ofsecond passage holes 223′ formed on the second bottom tank panel 221′,wherein the cooling water 1 dropping from the first fill material unit245′ is arranged to be collected at the second water collection basin22′ and reaches the second cooling unit 25′ through the second passageholes 223′.

The second cooling unit 25′ further comprises a second supporting tray256′ having a second tray partition member 2563′ upwardly extended froma bottom surface thereof for dividing the second supporting tray 256′into a third tray section 2561′ and a fourth tray section 2562′, whereintwo of the heat exchanging pipes 251′,252′ (i.e. the fifth heatexchanging pipe 251′ and the sixth heat exchanging pipe 252′) arespacedly supported in the third tray section 2561′ and two of the heatexchanging pipes 253′, 254′ (i.e. the seventh heat exchanging pipe 253′and the eighth heat exchanging pipe 254′) are spacedly supported in thefourth tray section 2562′.

The second fill material unit 255′ comprises a third fill material pack2551′ and a fourth fill material pack 2552′ spacedly supported in thetower housing 200′, wherein the cooling water 1 coming from the firsttray section 2461′ is arranged to drop into the third fill material pack2551′, while the cooling water 1 coming from the second lower traysection 2562′ is arranged to drop into the fourth fill material pack2552′.

In this alternative mode, the air is arranged to pass through the firstfill material unit 245′ and the second fill material unit 255′ and thefirst through eighth heat exchanging pipes 241′, 242′, 243′, 244′, 251′,252′, 253′, 254′ for transferring the heat from the cooling water 1 tothe air flowing through the multiple effect evaporative condenser 100′.

Moreover, the first cooling unit 24′ further comprises a plurality offirst water film distributors 247′ provided with the first throughfourth heat exchanging pipes 241′, 242′, 243′, 244′ respectively forguiding the cooling water 1 flowing through the first through fourthheat exchanging pipes 241′, 242′, 243′, 244′ in form of thin water filmthere along. The cooling water 1 in the thin water film state isarranged to perform heat exchange with the refrigerant 3 flowing throughthe first through fourth heat exchanging pipes 241′, 242′, 243′, 244′.

The cooling water 1 is then collected at the first supporting tray 246′which further has a plurality of through first passing holes 2467′formed thereon wherein the cooling water 1 collected at the firstsupporting tray 246′ is allowed to flow into the first fill materialunit 245′. Similarly, the second supporting tray 256′ further has aplurality of second lower passing holes 2567′ formed thereon wherein thecooling water 1 collected at the second supporting tray 256′ is allowedto flow into the second fill material unit 255′.

Moreover, the second cooling unit 25′ further comprises a plurality ofsecond water film distributors 257′ provided with the fifth througheighth heat exchanging pipes 251′, 252′, 253′, 254′ respectively forguiding the cooling water 1 flowing through the fifth through eighthheat exchanging pipes 251′, 252′, 253′, 254′ in thin water filmtherealong. The cooling water 1 in the thin water film state is arrangedto perform heat exchange with the refrigerant 3 flowing through thefifth through eighth heat exchanging pipes 251′,252′,253′,254′.

FIG. 10 to FIG. 11 illustrate that each of the multiple-effectevaporative condensers 100′ comprises an addition (i.e. third) coolingunit 26′ which is provided underneath the second cooling unit 25′ and isstructurally identical to the first cooling unit 24′ and the secondcooling unit 25′. Thus, each of the multiple-effect evaporativecondensers 100′ comprises a fourth water collection basin 28′ providedunderneath the third cooling unit 26′ for collecting the cooling water 1coming from the third cooling unit 26′.

The third cooling unit 26′ comprises a third supporting tray 266′ havinga tray partition member 2663′ upwardly extended from a bottom surfacethereof for dividing the third supporting tray 266′ into a fifth traysection 2661′ and a sixth tray section 2662′, wherein two of the heatexchanging pipes 261′, 262′ (i.e. the ninth heat exchanging pipe 261′and the tenth heat exchanging pipe 262′) are spacedly supported in thefifth tray section 2661′ and two of the heat exchanging pipes 263′, 264′(i.e. the eleventh heat exchanging pipe 263′ and the twelfth heatexchanging pipe 264′) are spacedly supported in the sixth tray section2662′.

The third cooling unit 26′ further comprises a third fill material unit265′ which comprises a fifth fill material pack 2651′ and a sixth fillmaterial pack 2652′ spacedly supported in the tower housing 200′,wherein the cooling water 1 coming from the fifth tray section 2661′ isarranged to drop into the fifth fill material pack 2651′, while thecooling water 1 coming from the sixth tray section 2662′ is arranged todrop into the sixth fill material pack 2652′.

Moreover, the third cooling unit 26′ further comprises a plurality ofthird water film distributors 267′ provided with the ninth throughtwelfth heat exchanging pipes 261′, 262′, 263′, 264′ respectively forguiding the cooling water 1 flowing through the ninth through twelfthheat exchanging pipes 261′, 262′, 263′, 264′ in thin water filmtherealong. The cooling water 1 in the thin water film state is arrangedto perform heat exchange with the refrigerant 3 flowing through theninth through twelfth heat exchanging pipes 261′, 262′, 263′, 264′.

On the other hand, the third water collection basin 23′ has a thirdbottom tank panel 231′, a second side tank: panel 232′, a plurality ofthrough third passage holes 233′ formed on the third bottom tank: panel231′, wherein the cooling water 1 dropping from the second fill materialunit 255′ is arranged to be collected at the third water collectionbasin 23′ and reaches the third cooling unit 26′ through the thirdpassage holes 233′. The cooling water 1 passing through the thirdcooling unit 26′ is arranged to be collected in the fourth watercollection basin 28′ and is pumped back to the first water collectionbasin l′ for another cycle of heat exchange with the refrigerant 3.

As shown in FIG. 11 to FIG. 13 of the drawings, each of the heatexchanging pipes 240′ (241′-244′) is embodied to be manufactured to forma three-dimensional pipe array extending in the multiple effectevaporative condenser 100′. Thus, each of the heat exchanging pipes241′-244′ comprises a first horizontal section 2401′ horizontallyextending in the tower housing 200′, a second horizontal section 2402′horizontally extending in the tower housing 200′ at a positionunderneath the first horizontal section 2401′, and a plurality ofvertical sections 2403′ extended between the first horizontal section2401′ and the second horizontal section 2402′, wherein the refrigerant 3is arranged to flow from the second horizontal section 2402′ to thefirst horizontal section 2401′ through the vertical sections 2403′. Therefrigerant 3 flowing through the second horizontal section 2402′ of oneparticular heat exchanging pipe 240′ is then guided to flow into thesecond horizontal section 2402′ of an adjacent heat exchanging pipe240′.

As shown in FIG. 14 of the drawings, each of the multiple effectevaporative condenser 100′ comprises only the first cooling unit 24′ sothat the cooling water 1 coming from the first fill material unit 245′is collected at the second water collection basin 22′ and is pumped backto the first water collection basin 21′.

Referring to FIG. 15A to FIG. 15C of the drawings, a second alternativemode of the multiple-effect evaporative condenser 100″ is illustrated.FIG. 15 illustrates that the multiple-effect evaporator condenser 100′in its second alternative mode and comprises a first cooling unit 24″and a second cooling unit 25″. The second alternative mode of themultiple-effect evaporative condenser 100″ is similar to the abovealternative modes of the preferred embodiment except the cooling units24″ (25″). In this second alternative mode, the first cooling unit 24″comprises three of the heat exchanging pipes 240″ (i.e. the firstthrough third heat exchanging pipes 241″, 242″, 243″) while the secondcooling unit 25″ comprises another three of the heat exchanging pipes240″ (i.e. the fourth through sixth heat exchanging pipes 251 “, 252”,253″).

The first through third heat exchanging pipes 241″, 242″, 243″ areimmersed into the first water collection basin 21″ which is communicatedwith the pumping device 10″ so that cooling water 1 is first pumped intothe first water collection basin 21″ for performing heat exchange withthe refrigerant 3 flowing through the first through third heatexchanging pipes 241 “, 242”, 243″. The cooling water 1 flowing throughthe first through the first through third heat exchanging pipes 241″,242″, 243″ are arranged to flow through the upper fill material unit245″ which comprises a first fill material pack 2451″ for performingheat exchange with the air drawn from the air inlet 201.

Furthermore, the fourth through sixth heat exchanging pipes 251″, 252″,253″ are immersed into the second water collection basin 22″ so thatcooling water 1″ coming from the first cooling unit 24″ is arranged toperform heat exchange with the refrigerant 3 flowing through the fourththrough sixth heat exchanging pipes 251″,252″,253″.

In this second alternative mode of the multiple effect evaporativecondenser of the present invention, the first cooling unit 24″ furthercomprises a first supporting tray 246″, and the first water collectionbasin 21″ comprises a first tank body 211″ defining a first tank cavity2111″ for receiving the cooling water 1, and a plurality of first watertubes 212″ spacedly formed in the first tank body 211″ to define aplurality of first water channels 2121″ within the first water tubes212″ respectively, The first water tubes 212″ communicates the firsttank cavity 2111″ with the first fill material unit 245″ through thefirst supporting tray 246″ so that cooling water 1 is capable of flowingfrom the first water collection basin 21″ to the first supporting tray246″ through the first water channels 2121″.

The cooling water 1 is then collected at the first supporting tray 246″which further has a plurality of through first passing holes 2467″formed thereon wherein the cooling water 1 collected at the uppersupporting tray 246″ is allowed to flow into the first fill materialunit 245″ for performing heat exchange with the air drawn from the airinlet 201.

It is worth mentioning that each of the first water tubes 212″ ismounted in the first water collection basin 21″ in such a manner that atop opening of the first water tube 212″ is higher than the firstthrough third heat exchanging pipes 241″, 242″, 243″. From simplephysics, the cooling water 1 having higher temperature tends to go up inthe first water collection basin 21″ while the cooling water 1 havingrelatively lower temperature tends to go down in the first watercollection basin 21″, Thus, the cooling water 1 in the first watercollection basin 21″ is arranged to absorb heat from the first throughthird heat exchanging pipes 241″, 242″, 243″, and after heat absorption,the cooling water 1 goes up in the first water collection basin 21″ andflow into one of the first water tubes 212″, Relatively cool coolingwater 1 is retained in the lower portion of the first water collectionbasin 21″ for heat absorption until the temperature increases to such anextent that the cooling water 1 goes up in the first water collectionbasin 21″ and enters the first water tubes 212″.

The second cooling unit 25″ further comprises a second supporting tray256″, and the second water collection basin 22″ comprises a second tankbody 221″ defining a second tank cavity 2211″ for receiving the coolingwater 1 coming from the first cooling unit 24″, and a plurality ofsecond water tubes 222″ spacedly formed in the second tank body 221″ todefine a plurality of second water channels 2221″ within the secondwater tubes 222″ respectively, The second water tubes 222″ communicatethe second tank cavity 2211″ with the second fill material pack 2551″ ofthe lower fill material unit 255″ so that cooling water 1 is capable offlowing from the second water collection basin 22″ to the secondsupporting tray 256″ through the second water channels 2221″.

The cooling water 1 is then collected at the second supporting tray 256″which further has a plurality of through second passing holes 2567″formed thereon wherein the cooling water 1″ collected at the secondsupporting tray 256″ is allowed to flow into the second fill materialpack 2551″ of the second fill material unit 255″ for performing heatexchange with the air drawn from the air inlet 202.

As in the case of the first water collection basin 21″, each of thesecond water tubes 222″ is mounted in the second water collection basin22″ in such a manner that a top opening of the second water tube 222″ ishigher than the fourth through sixth heat exchanging pipes 251″, 252″,253″, The cooling water 1 in the second water collection basin 22″ isarranged to absorb heat from the fourth through sixth heat exchangingpipes 251″, 252″, 253″, and after heat absorption, the cooling water 1goes up in the second water collection basin 22″ and flow into one ofthe second water tubes 222″, Relatively cool cooling water 1 is retainedin the lower portion of the second water collection basin 22″ for heatabsorption until the temperature increases to such an extent that thecooling water 1″ goes up in the second water collection basin 22″ andenters the second water tubes 222″.

The second supporting tray 256″ further has a plurality of through lowerpassing holes 2567″ formed thereon wherein the cooling water 1 collectedat the second supporting tray 256″ is allowed to flow into the secondfill material unit 255″.

The second water collection basin 22″ further comprises a water guider229″ inclinedly extended in the second tank cavity 2211″ in such amanner that the cooling water 1 coming from the first cooling unit 24″is guided to flow into the second water collection basin 22″ through thewater guider 229″ for performing heat exchange with the fourth throughsixth heat exchanging pipes 251″, 252″, 253″.

Referring to FIG. 16, FIG. 17 A to FIG. 17C, FIG. 18A to FIG. 18C of thedrawings, a third alternative mode of the above preferred embodiment ofthe multiple-effect evaporative condenser 100A of the present inventionis illustrated. FIG. 16 illustrates that the multiple-effect evaporatorcondenser 100A in its third alternative mode and comprises a firstcooling unit 24A, a second cooling unit 25A and a third cooling unit26A. The third alternative mode of the multiple-effect evaporativecondenser 100A is similar to the second alternative mode just described.In this third alternative mode, each of the first cooling unit 24A, thesecond cooling unit 25A and the third cooling unit 26A comprises five ofthe heat exchanging pipes 240A.

Moreover, the first cooling unit 24A further comprises a firstrefrigerant inlet pipe 248A connected to the heat exchanger 30, and afirst refrigerant outlet pipe 249A, wherein the corresponding heatexchanging pipes 240A are extended between the first refrigerant inletpipe 248A and the first refrigerant outlet pipe 249A. Similarly, thesecond cooling unit 25A further comprises a second refrigerant inletpipe 258A connected to the first refrigerant outlet pipe 249A, and asecond refrigerant outlet pipe 259A, wherein the corresponding heatexchanging pipes 240A are extended between the second refrigerant inletpipe 258A and the second refrigerant outlet pipe 259A. Moreover, thethird cooling unit 26A further comprises a third refrigerant inlet pipe268A connected to the second refrigerant outlet pipe 259A, and a thirdrefrigerant outlet pipe 269A connected to the heat exchanger 30, whereinthe corresponding heat exchanging pipes 240A are extended between thethird refrigerant inlet pipe 268A and the third refrigerant outlet pipe259A. In other words, for each of the first cooling unit 24A through thethird cooling unit 26A, the corresponding heat exchanging pipes 240A andthe corresponding refrigerant inlet 248A (258A) (268A) and thecorresponding refrigerant outlet pipe 249A (259A) (269A) form threearray of pipes for transmitting the refrigerant 3 which is arranged toperform heat exchange with the cooling water 1 passing through the firstcooling unit 24A to the third cooling unit 26A.

The refrigerant 3 entering the first refrigerant inlet pipe 248A isbifurcated to flow into the five heat exchanging pipes 240A in the firstcooling unit 24A. The heat exchanging pipes 240A are immersed into thefirst water collection basin 21 A which is communicated with the pumpingdevice 10 so that cooling water 1 is first pumped into the first watercollection basin 21A for performing heat exchange with the refrigerant 3flowing through the heat exchanging pipes 240A. The cooling water 1flowing through these heat exchanging pipes 240A are arranged to flowthrough the first fill material unit 245A which comprises a first fillmaterial pack 2451A for performing heat exchange with the air drawn fromthe air inlet 201.

Note that the refrigerant 3 passing through the heat exchanging pipes240A of the first cooling unit 24A is collected to flow into the firstrefrigerant outlet pipe 249A, which is connected to the secondrefrigerant inlet pipe 258A. The refrigerant 3 entering the secondrefrigerant inlet pipe 258A is bifurcated to flow into the five heatexchanging pipes 240A in the second cooling unit 25A.

Furthermore, the heat exchanging pipes 240A in the second cooling unit25A are immersed into the second water collection basin 221A so thatcooling water 1 coming from the first cooling unit 24A is arranged toperform heat exchange with the refrigerant 3 flowing through the heatexchanging pipes 240A of the second cooling unit 25A. The refrigerant 3passing through the heat exchanging pipes 240A of the second coolingunit 25A is collected to flow into the second refrigerant outlet pipe259A, which is connected to the third refrigerant inlet pipe 268A.

In this third alternative mode, the first cooling unit 24A furthercomprises a first supporting tray 246A, and the first water collectionbasin 21 A comprises a first tank body 211A defining a first tank cavity2111A for receiving the cooling water 1, and a plurality of first watertubes 212A spacedly formed in the first tank body 211 A to define aplurality of first water channels 2121A within the first water tubes212A respectively. The first water tubes 212A communicate the first tankcavity 2111A with the first fill material unit 245A so that coolingwater 1 is capable of flowing from the first water collection basin 21Ato the first supporting tray 246A through the first water channels2121A.

The cooling water 1 then passes through the first supporting tray 246Awhich further has a plurality of through first passing holes 2467 Aformed thereon wherein the cooling water 1 reaching the first supportingtray 246A is allowed to flow into the first fill material unit 245A forperforming heat exchange with the air drawn from the air inlet 201.

It is worth mentioning that each of the first water tubes 212A ismounted in the first water collection basin 21A in such a manner that atop opening of the first water tube 212A is higher than thecorresponding heat exchanging pipes 240A. From simple physics, thecooling water 1 having higher temperature tends to go up in the firstwater collection basin 21 A while the cooling water 1 having relativelylower temperature tends to go down in the first water collection basin21A. Thus, the cooling water 1 in the first water collection basin 21Ais arranged to absorb heat from the heat exchanging pipes 240A, andafter heat absorption, the cooling water 1 goes up in the first watercollection basin 21A and flow into one of the first water tubes 212A.Relatively cool cooling water 1 is retained in the lower portion of thefirst water collection basin 21A for heat absorption until thetemperature increases to such an extent that the cooling water 1 goes upin the first water collection basin 21 A and enters the first watertubes 212A.

The second cooling unit 25A further comprises a second supporting tray256A, and the second water collection basin 22A comprises a second tankbody 221A defining a second tank cavity 2211A for receiving the coolingwater 1 coming from the first cooling unit 24A, and a plurality ofsecond water tubes 222A spacedly formed in the second tank body 221A todefine a plurality of second water channels 2221A within the secondwater tubes 222A respectively. The second water tubes 222A communicatethe second tank cavity 2211A with the second fill material unit 255Awhich comprises a second fill material pack 2551A so that cooling water1 is capable of flowing from the second water collection basin 22A tothe second supporting tray 256A through the second water channels 2221A.

The cooling water 1 is then collected at the second supporting tray 256Awhich further has a plurality of through second passing holes 2567 Aformed thereon wherein the cooling water 1 collected at the secondsupporting tray 256A is allowed to flow into the second fill materialpack 2551A of the second fill material unit 255A for performing heatexchange with the air drawn from the air inlet 202.

As in the case of the first water collection basin 21A, each of thesecond water tubes 222A is mounted in the second water collection basin22A in such a manner that a top opening of the second water tube 222A ishigher than the corresponding heat exchanging pipes 240A. The coolingwater 1′ in the second water collection basin 22A is arranged to absorbheat from the heat exchanging pipes 240A, and after heat absorption, thecooling water 1 goes up in the second water collection basin 22A andflow into one of the second water tubes 222A. Relatively cool coolingwater 1 is retained in the lower portion of the second water collectionbasin 22A for heat absorption until the temperature increases to such anextent that the cooling water 1 goes up in the second water collectionbasin 22A and enters the second water tubes 222A.

The second water collection basin 22A further comprises a first waterguider 229A inclinedly extended in the second tank cavity 2211A in sucha manner that the cooling water 1 coming from the first cooling unit 24Ais guided to flow into a lower portion of the second water collectionbasin 22A through the first water guider 229A for performing heatexchange with the heat exchanging pipes 240A. Note that the first waterguider 229A is mounted above second water tubes 222A so that the coolingwater 1 coming from the first cooling unit 24A is not mixed with thecooling water 1 which has absorbed heat from the heat exchanging pipes240A.

As shown in FIG. 18A to FIG. 18C of the drawings, the first water guider229A has a first inclined portion 2291A inclinedly extended from the topside edge portion of the second water collection basin 22A to anopposite side portion of the second water collection basin 22A forguiding the cooling water 1 coming from the first fill material unit245A to slide inclinedly on the first inclined portion 2291A, and afirst guiding portion 2292A downwardly and substantially verticallyextended from the first inclined portion 2291 A to the second tankcavity 2211 A so that the cooling water 1 sliding on the first inclinedportion 2291 A and having a relatively cool temperature is guided toflow into a lower portion of the second tank cavity 2211A and performheat exchange with the heat exchanging pipes 240A.

The third cooling unit 26A further comprises a third supporting tray266A, and the third water collection basin 23A comprises a third tankbody 231A defining a third tank cavity 2311A for receiving the coolingwater 1 coming from the second cooling unit 25A, and a plurality ofthird water tubes 232A spacedly formed in the third tank body 231A todefine a plurality of third water channels 2321A within the third watertubes 232A respectively. The third water tubes 232A communicate thethird tank cavity 2311A with the third fill material unit 265A whichcomprises a third fill material pack 2651A so that cooling water I iscapable of flowing from the third water collection basin 23A to thethird supporting tray 266A through the third water channels 2321A.

The cooling water 1 is then collected at the third supporting tray 266Awhich further has a plurality of through third passing holes 2667 Aformed thereon wherein the cooling water 1 collected at the thirdsupporting tray 266A is allowed to flow into the third fill materialpack 2651A of the third fill material unit 265A for performing heatexchange with the air drawn from the air inlet 202.

As in the case of the second water collection basin 22A, each of thethird water tubes 232A is mounted in the third water collection basin23A in such a manner that a top opening of the third water tube 232A ishigher than the corresponding heat exchanging pipes 240A. The coolingwater 1 in the third water collection basin 23A is arranged to absorbheat from the heat exchanging pipes 240A, and after heat absorption, thecooling water 1 goes up in the third water collection basin 23A and flowinto one of the third water tubes 232A. Relatively cool cooling water 1is retained in the lower portion of the third water collection basin 23Afor heat absorption until the temperature increases to such an extentthat the cooling water 1 goes up in the third water collection basin 23Aand enters the third water tubes 232A.

The third collection basin 23A further comprises a second water guider230A inclinedly extended in the third tank cavity 2311A in such a mannerthat the cooling water 1 coming from the second cooling unit 25A isguided to flow into a lower portion of the third water collection basin23A through the second water guider 230A for performing heat exchangewith the heat exchanging pipes 240A. Note that the second water guider230A is mounted above third water tubes 232A so that the cooling water 1coming from the second cooling unit 25A is not mixed with the coolingwater 1 which has absorbed heat from the heat exchanging pipes 240A.

The second water guider 230A has a second inclined portion 2301Ainclinedly extended from the top side edge portion of the third watercollection basin 23A to an opposite side portion of the third watercollection basin 23A for guiding the cooling water 1 coming from thesecond fill material unit 255A to slide inclinedly on the secondinclined portion 2301A, and a second guiding portion 2302A downwardlyand substantially vertically extended from the second inclined portion2301A to the third tank cavity 2311A so that the cooling water 1 slidingon the second inclined portion 2301A and having a relatively cooltemperature is guided to flow into a lower portion of the third tankcavity 2311A and perform heat exchange with the heat exchanging pipes240A.

Referring to FIG. 19 to FIG. 20 of the drawings, a fourth alternativemode of the multiple effect evaporative condenser according to thepreferred embodiment of the present invention is illustrated. The fourthalternative mode is similar to the above described alternative modes.According to the fourth alternative mode, the multiple effectevaporative condenser 100B also comprises a tower housing 200 (as shownin FIG. 3) having an air inlet 201 and an air outlet 202, a first watercollection basin 21B, a first cooling unit 24B, a second cooling unit25B, and a second water collection basin 22B provided underneath thesecond cooling unit 25B.

The first water collection basin 21B is mounted in the tower housing 200(as shown in FIG. 3) for collecting the cooling water 1 pumped from thepumping device 10. On the other hand, the first cooling unit 24Bcomprises a plurality of heat exchanging pipes 240B and a first fillmaterial unit 245B, wherein the cooling water 1 collected in the firstwater collection basin 21B is arranged to flow through exterior surfacesof the heat exchanging pipes 240B and the first fill material unit 245B.

On the other hand, the second cooling unit 25B comprises a plurality ofheat exchanging pipes 240B and a predetermined amount of second fillmaterial unit 255B, wherein the cooling water 1 passing through thefirst fill material unit 245B is arranged to flow through exteriorsurfaces of the heat exchanging pipes of the second cooling unit 25B,and the second fill material unit 255B.

The second water collection basin 22B is positioned underneath thesecond cooling unit 25B for collecting the cooling water 1 flowing fromthe second cooling unit 25B, wherein the cooling water 1 collected inthe second water collection basin 22B is arranged to be pumped back tothe first water collection basin 21B by the pumping device 10, whereinthe refrigerant 3 is arranged to flow through the heat exchanging pipesof the first cooling unit 24B and the second cooling unit 25B in such amanner and flow sequence that the refrigerant 3 is arranged to performheat exchange with the cooling water 1 flowing through the multipleeffect evaporative condenser 100B for lowering a temperature of therefrigerant 3, wherein the predetermined amount of air is sucked intothe tower housing 200 (as shown in FIG. 3) through the air inlet 201Bfor performing heat exchange with the cooling water 1 flowing throughthe first cooling unit 24B and the second cooling unit 25B for loweringa temperature of the cooling water 1, wherein the air having absorbedthe heat from the cooling water 1 is discharged out of the multipleeffect evaporative condenser 100B through the air outlet 202B.

The first water collection basin 21B has a first bottom tank panel 211B,a first side tank panel 212B, a plurality of through first passage holes213B formed on the bottom tank panel 211 B, wherein the cooling water 1is arranged to be pumped into the first water collection basin 21 B andreach the first cooling unit 24B through the first passage holes 213B.

As shown in FIG. 19 to FIG. 20 of the drawings, the heat exchangingpipes 240B of the first cooling unit 24B and the second cooling unit 25Bare spacedly extended in the tower housing 200 (as shown in FIG. 3).Moreover, the first cooling unit 24B further comprises a firstrefrigerant inlet pipe 248B connected to the heat exchanger 30 (as shownin FIG. 8), and a first refrigerant outlet pipe 249B, wherein thecorresponding heat exchanging pipes 240B are extended between the firstrefrigerant inlet pipe 248B and the first refrigerant outlet pipe 249B.Similarly, the second cooling unit 25B further comprises a secondrefrigerant inlet pipe 258A connected to the heat exchanger 30 (as shownin FIG. 8), and a second refrigerant outlet pipe 259A, wherein thecorresponding heat exchanging pipes 240B are extended between the secondrefrigerant inlet pipe 258B and the second refrigerant outlet pipe 259B.

The refrigerant 3 leaving the compressor 40 (as shown in FIG. 8) firstenters the first refrigerant inlet pipe 248A, which is connected to theheat exchanging pipes 240B (i.e. the first through fifth heat exchangingpipes 241B, 242B, 243B, 244B, 245B as shown in FIG. 20) of the firstcooling unit 24B. As shown in FIG. 20 of the drawings, the refrigerant 3is then guided to flow into the first heat exchanging pipe 241 B and thesecond heat exchanging pipe 242B and reaches the first refrigerantoutlet pipe 249B, which collects the refrigerant 3 from the first heatexchanging pipe 241B and the second heat exchanging pipe 242B.

The refrigerant 3 is then guided to flow into the third heat exchangepipe 243B and the fourth heat exchanging pipe 244B and reaches the firstrefrigerant inlet pipe 248B. The refrigerant 3 flowing through the thirdheat exchange pipe 243C and the fourth heat exchanging pipe 244B is thencollected at the first refrigerant inlet pipe 248B and guided to flowinto the fifth heat exchanging pipe 245B. The refrigerant 3 flowingthrough the fifth heat exchanging pipe 245B is then collected at thefirst refrigerant outlet pipe 249B, and the refrigerant is guided toflow out of the first cooling unit 24B.

It is worth mentioning that each of the first refrigerant inlet pipe248B and the first refrigerant outlet pipe 249B comprises a blockingmember 2481B, 2491B mounted therein for guiding the refrigerant 3sequentially flowing in the path described above.

In other words, the refrigerant 3 entering the first cooling unit 24Bfirst enters the first refrigerant inlet pipe 248B and hits the blockingmember 2481B provided therein. The refrigerant 3 hitting the blockingmember 2481 B is guided to flow into the first heat exchanging pipe 241Band the second heat exchanging pipe 242B and reaches the firstrefrigerant outlet pipe 249B. The refrigerant 3 reaching the firstrefrigerant outlet pipe 249B is arranged to hit the blocking member2491B provided therein and is guided to flow into the third heatexchanging pipe 243B and the fourth heat exchanging pipe 244B andreaches the first refrigerant inlet pipe 248A. The refrigerant 3reaching the first refrigerant inlet pipe 248A is blocked by theblocking member 2481B and prevented from going back to the first heatexchanging pipe 241B and the second heat exchanging pipe 242B. Therefrigerant 3 is then guided to flow into the fifth heat exchanging pipe245B. The refrigerant 3 flowing through the fifth heat exchanging pipe245B is prevented from flowing back into the fourth heat exchanging pipe244B and the third heat exchanging pipe 243B by the blocking member2491B of the first refrigerant outlet pipe 249B.

Also referring to FIG. 19 to FIG. 20 of the drawings, the refrigerant 3leaving the first cooling unit 24B flows out of the multiple effectevaporative condenser 100B. On the other hand, refrigerant 3 from thecompressor 40 (as shown in FIG. 8) or other like component of the airconditioning system is also guided to enter the second cooling unit 25B.The refrigerant 3 is guided to flow into the second refrigerant inletpipe 258B, and then is guided to flow into the sixth heat exchangingpipe 251B and the seventh heat exchanging pipe 252B and reaches thesecond refrigerant outlet pipe 259B, which collects the refrigerant 3from the sixth heat exchanging pipe 251B and the seventh heat exchangingpipe 252B.

Moreover, the refrigerant 3 is then guided to flow into the eighth heatexchange pipe 253B and the ninth heat exchanging pipe 254B and reachesthe second refrigerant inlet pipe 258B. The refrigerant 3 flowingthrough the eighth heat exchange pipe 253B and the ninth heat exchangingpipe 254B is then collected at the second refrigerant inlet pipe 258Band guided to flow into the tenth heat exchanging pipe 255B. Therefrigerant 3 flowing through the tenth heat exchanging pipe 255B isthen collected at the second refrigerant outlet pipe 259B, and therefrigerant is guided to flow out of the second cooling unit 25B.

It is worth mentioning that each of the second refrigerant inlet pipe258B and the second refrigerant outlet pipe 259B comprises a blockingmember 2581B, 2591B mounted therein for guiding the refrigerant 3sequentially flowing in the path described above.

In other words, the refrigerant 3 entering the second cooling unit 25Bfirst enters the second refrigerant inlet pipe 258B and hits theblocking member 2581B provided therein. The refrigerant 3 hitting theblocking member 2581B is guided to flow into the sixth heat exchangingpipe 251B and the seventh heat exchanging pipe 252B, and reaches thesecond refrigerant outlet pipe 259B. The refrigerant 3 reaching thesecond refrigerant outlet pipe 259B is arranged to hit the blockingmember 2591B provided therein and is guided to flow into the eighth heatexchanging pipe 253B and the ninth heat exchanging pipe 254B and reachesthe second refrigerant inlet pipe 258B. The refrigerant 3 reaching thesecond refrigerant inlet pipe 258B is blocked by the blocking member2581B and prevented from going back to the sixth heat exchanging pipe251B and the seventh heat exchanging pipe 252B. The refrigerant 3 isthen guided to flow into the tenth heat exchanging pipe 255B. Therefrigerant 3 flowing through the tenth heat exchanging pipe 255B isprevented from flowing back into the eighth heat exchanging pipe 253Band the ninth heat exchanging pipe 254B by the blocking member 2591B ofthe second refrigerant outlet pipe 259B.

As shown in FIG. 22 to FIG. 23 of the drawings, a fifth alternative modeof the multiple effect evaporative condenser according to the preferredembodiment of the present invention is illustrated. The fifthalternative mode is similar to the above described alternative modes.According to the fifth alternative mode, the multiple effect evaporativecondenser comprises a first cooling unit 24C, the second cooling unit25C and a third cooling unit 26C.

Moreover, the multiple-effect evaporative condenser 100C comprises threepumping devices 10, a first water collection basin 21 C, a second watercollection basin 22C, and a plurality of basin partitioning plates 27Cprovided in the first water collection basin 21 C and the second watercollection basin 22C respectively.

The basin partitioning plates 27C spacedly provided in the first watercollection basin 21C divide the first water collection basin 21C intofirst through third water collection compartments 216C, 217C, 218C.Similarly, the basin partitioning plates 27C provided in the secondwater collection basin 22C divide the second water collection basin 22Cinto fourth through sixth water collection compartment 226C, 227C, 228C.

In this fifth alternative mode, the first cooling unit 24C comprises afirst fill material unit 245C which comprises first through third fillmaterial pack 2451 C, 2452C, 2453C. The second cooling unit 25Ccomprises a second fill material unit 255C which comprises fourththrough sixth fill material pack 2551 C, 2552C, 2553C. The third coolingunit 26C comprises a third fill material unit 265C which comprisesseventh through ninth fill material pack 2651 C, 2652C, 2653C.

The cooling water 1 is first collected at the first water collectionbasin 21 C, which are partitioned into first through third watercollection compartments 216C, 217C, 218C. The cooling water 1 collectedin the first water collection compartment 216C is arranged to flowthrough the first cooling unit 24C, the second cooling unit 25C, thethird cooling unit 26C and is finally collected in the fourth watercollection compartment 226C of the second water collection basin 22C.Similarly, the cooling water 1 collected in the second water collectioncompartment 217C is arranged to flow through the first cooling unit 24C,the second cooling unit 25C, the third cooling unit 26C and is finallycollected in the fifth water collection compartment 227C of the secondwater collection basin 22C. Moreover, the cooling water 1 collected inthe third water collection compartment 218C is arranged to flow throughthe first cooling unit 24C, the second cooling unit 25C, the thirdcooling unit 26C and is finally collected in the sixth water collectioncompartment 228C of the second water collection basin 22C.

As shown in FIG. 22 of the drawings, each of the pumping devices 10 isarranged to pump the cooling water 1 circulating between twocorresponding water collection compartments of the first watercollection basin 21 C and the second water collection basin 22C.

The first cooling unit 24 comprises nine heat exchanging pipes 240C(i.e. the first through ninth heat exchanging pipe 2401C, 2402C, 2403C,2404C, 2405C, 2406C, 2407C, 2408C, 2409C), wherein the cooling water 1collected at the first water collection compartment 216C is arranged toflow through, sequentially, the first through third heat exchanging pipe2401 C, 2402C, 2403C, the first fill material pack 2451 C, tenth throughtwelfth heat exchanging pipe 2501C, 2502C, 2503C, the fourth fillmaterial pack 2551C, nineteenth through twenty first heat exchangingpipe 2601 C, 2602C, 2603C and the fourth water collection compartment226C.

Similarly, the cooling water 1 collected at the second water collectioncompartment 217C is arranged to flow through, sequentially, the fourththrough sixth heat exchanging pipe 2404C, 2405C, 2406C, the second fillmaterial pack 2452C, thirteenth through fifteenth heat exchanging pipe2504C, 2505C, 2506C, the fifth fill material pack 2552C, twenty secondthrough twenty fourth heat exchanging pipe 2604C, 2605C, 2606C and thefifth water collection compartment 227C.

Furthermore, the cooling water 1 collected at the third water collectioncompartment 218C is arranged to flow through, sequentially, the sevenththrough ninth heat exchanging pipe 2407C, 2408C, 2409C, the third fillmaterial pack 2453C, sixteenth through eighteenth heat exchanging pipe2507C, 2508C, 2509C, the sixth fill material pack 2553C, twenty fifththrough twenty seventh heat exchanging pipe 2607C, 2608C, 2609C and thesixth water collection compartment 228C.

As shown in FIG. 23 of the drawings, the first cooling unit 24C furthercomprises a first refrigerant inlet pipe 248C connected to the heatexchanger 30 (as shown in FIG. 8), and a first refrigerant outlet pipe249C, wherein the corresponding heat exchanging pipes (first throughninth heat exchanging pipes 2401C, 2402C, 2403C, 2404C, 2405C, 2406C,2407C, 2408C, 2409C) are extended between the first refrigerant inletpipe 248C and the first refrigerant outlet pipe 249C.

Similarly, as shown in FIG. 24 of the drawings, the second cooling unit25C further comprises a second refrigerant inlet pipe 258C connected tothe heat exchanger 30, and a second refrigerant outlet pipe 259C,wherein the corresponding heat exchanging pipes (tenth heat througheighteenth heat exchanging pipe 2501C, 2502C, 2503C, 2504C, 2505C,2506C, 2507C, 2508C, 2509C) are extended between the second refrigerantinlet pipe 258C and the second refrigerant outlet pipe 259C.

Furthermore, as shown in FIG. 25 of the drawings, the third cooling unit26C further comprises a second refrigerant inlet pipe 268C connectedalso to the heat exchanger 30, and a second refrigerant outlet pipe269C, wherein the corresponding heat exchanging pipes (nineteenththrough twenty-seventh heat exchanging pipe (2601C, 2602C, 2603C, 2604C,2605C, 2606C, 2607C, 2608C, 2609C) are extended between the thirdrefrigerant inlet pipe 268C and the third refrigerant outlet pipe 269C.

As shown in FIG. 23 of the drawings, each of the first refrigerant inletpipe 248C and the first refrigerant outlet pipe 249C comprises ablocking member 2481B, 2491B mounted therein for guiding the refrigerant3 sequentially flowing in the path described below.

In other words, the refrigerant 3 from the heat exchanger 30 enteringthe first cooling unit 24C first enters the first refrigerant inlet pipe248C and hits the blocking member 2481C provided therein. Therefrigerant 3 hitting the blocking member 2481C is guided to flow intothe first heat exchanging pipe 2401C, the second heat exchanging pipe2402C and the third heat exchanging pipe 2403C and reaches the firstrefrigerant outlet pipe 249C. The refrigerant 3 reaching the firstrefrigerant outlet pipe 249C is arranged to hit the blocking member2491B provided therein and is guided to flow into the fourth heatexchanging pipe 2404C, the fifth heat exchanging pipe 2405C and thesixth heat exchanging pipe 2406C and reaches the first refrigerant inletpipe 248C. The refrigerant 3 reaching the first refrigerant inlet pipe248C is blocked by the blocking member 2481 C and the refrigerant 3 isprevented from going back to the first through third heat exchangingpipe 2401C, 2402C, 2403C. The refrigerant 3 is then guided to flow intothe seventh heat exchanging pipe 2407C, the eighth heat exchanging pipe2408C, and the ninth heat exchanging pipe 2409C and the firstrefrigerant outlet pipe 249C. The refrigerant 3 is then arranged toleave the first cooling unit 24C and flow back to the heat exchanger 30.

As shown in FIG. 24 of the drawings, each of the second refrigerantinlet pipe 258C and the second refrigerant outlet pipe 259C comprises ablocking member 2581C, 2591C mounted therein for guiding the refrigerant3 sequentially flowing in the path described below.

In other words, the refrigerant 3 from the heat exchanger 30 (as shownin FIG. 8) enters the second refrigerant inlet pipe 258C, and therefrigerant 3 entering the second cooling unit 25C first enters thesecond refrigerant inlet pipe 258C and hits the blocking member 2581Cprovided therein. The refrigerant 3 hitting the blocking member 2581C isguided to flow into the tenth heat exchanging pipe 2501 C, the eleventhheat exchanging pipe 2502C and the twelfth heat exchanging pipe 2503Cand reaches the second refrigerant outlet pipe 259C. The refrigerant 3reaching the second refrigerant outlet pipe 259C is arranged to hit theblocking member 2591B provided therein and is guided to flow into thethirteenth heat exchanging pipe 2504C, the fourteenth heat exchangingpipe 2505C and the fifteenth heat exchanging pipe 2506C and reaches thesecond refrigerant inlet pipe 258C. The refrigerant 3 reaching thesecond refrigerant inlet pipe 258C is blocked by the blocking member2581 C and the refrigerant 3 is prevented from going back to the tenthheat exchanging pipe 2501C, the eleventh heat exchanging pipe 2502C andthe twelfth heat exchanging pipe 2503C. The refrigerant 3 is then guidedto flow into the sixteenth heat exchanging pipe 2507C, the seventeenthheat exchanging pipe 2508C, and the eighteenth heat exchanging pipe2509C and the second refrigerant outlet pipe 259C. The refrigerant 3 isthen arranged to leave the second cooling unit 25C and flow back to theheat exchanger 30.

At the same time, the refrigerant 3 from the heat exchange 30 (as shownin FIG. 8) also enters the third refrigerant inlet pipe 268C of thethird cooling unit 26C and hits the blocking member 2681 C providedtherein. The refrigerant 3 hitting the blocking member 2581 C is guidedto flow into the nineteenth heat exchanging pipe 2601 C, the twentiethheat exchanging pipe 2602C and the twenty first heat exchanging pipe2603C and reaches the third refrigerant outlet pipe 269C. Therefrigerant 3 reaching the third refrigerant outlet pipe 269C isarranged to hit the blocking member 2691B provided therein and is guidedto flow into the twenty second heat exchanging pipe 2604C, the twentythird heat exchanging pipe 2605C and the twenty fourth heat exchangingpipe 2606C and reaches the third refrigerant inlet pipe 268C. Therefrigerant 3 reaching the third refrigerant inlet pipe 268C is blockedby the blocking member 2681 C and the refrigerant 3 is prevented fromgoing back to the nineteenth heat exchanging pipe 260 I C, the twentiethheat exchanging pipe 2602C and the twenty first heat exchanging pipe2603C. The refrigerant 3 is then guided to flow into the twenty fifthheat exchanging pipe 2607C, the twenty sixth heat exchanging pipe 2608C,and the twenty seventh heat exchanging pipe 2609C and the thirdrefrigerant outlet pipe 269C. The refrigerant 3 is then arranged toleave the third cooling unit 26C and is guided to flow back to the heatexchanger 30.

Note that the refrigerant 3 described above may come from any othercomponents (not necessarily the heat exchanger 30), as long as heatexchange is necessary to lower the temperature of the refrigerant 3.This is a feature which enables the multiple effect evaporativecondenser 100C to be utilized in a wide variety of technical fields (andnot only air conditioning system).

Referring to FIG. 26A to FIG. 26C, FIG. 27, and FIG. 28A to FIG. 28C ofthe drawings, a sixth alternative mode of the multiple effectevaporative condenser 100D according to the above preferred embodimentof the present invention is illustrated. The sixth alternative mode issubstantially similar to the preferred embodiment.

FIG. 26 illustrates two multiple effect evaporative condenser 100D andeach of the multiple-effect evaporative condenser 100D is served by atleast one (preferably two) pumping device 10. In this sixth alternativemode, each of the multiple-effect evaporative condensers 100D comprisesa first water collection basin 21D, a first cooling unit 24D, a secondcooling unit 25D, a second water collection basin 22D positioned betweenthe first cooling unit 24D and the second cooling unit 25D, a thirdwater collection basin 23D, and a plurality of basin partitioning plates27D provided on the first water collection basin 21D, the second watercollection basin 22D, and the third water collection basin 23Drespectively.

The first cooling unit 24D comprise a plurality of heat exchanging pipes240D and a first fill material unit 245D provided underneath the heatexchanging pipes 240D, wherein the cooling water 1 collected in thefirst water collection basin 21D is arranged to flow through exteriorsurfaces of the heat exchanging pipes 240D and then through the firstfill material unit 245D.

The basin partitioning plates 27D provided on the first water collectionbasin 21D divides the first water collection basin 21D into first andsecond water collection compartments 216D, 217D. Similarly, the basinpartitioning plate 27C provided on the second water collection basin 22Ddivides the second water collection basin 22D into third and fourthwater collection compartment 226D, 227D. Moreover, the basinpartitioning plate 27D provided on the third water collection basin 23Ddivides the third water collection basin 23D into fifth and sixth watercollection compartment 236D, 237D.

In this sixth alternative mode, the first cooling unit 24D comprises afirst fill material unit 245D which comprises first and second fillmaterial pack 2451D, 2452D. The second cooling unit 25D comprises asecond fill material unit 255D which comprises third and fourth fillmaterial pack 2551D, 2552D.

The cooling water 1 is first collected at the first water collectionbasin 21D, which are partitioned into first and second water collectioncompartment 216D, 217D. The cooling water 1 collected in the first watercollection compartment 216D is arranged to flow through the firstcooling unit 24D, the third water collection compartment 226D of thesecond cooling unit 25D, and is finally collected in the fifth watercollection compartment 236D of the third water collection basin 23D.

Similarly, the cooling water 1 collected in the second water collectioncompartment 217D is arranged to flow through the first cooling unit 24D,the fourth water collection compartment 227D of the second cooling unit25D, and is finally collected in the sixth water collection compartment237D of the third water collection basin 23D.

The refrigerant 3 is arranged to follow at least one heat exchangingroute formed by the heat exchanging pipes 240D of the first cooling unit24D and the second cooling unit 25D.

The first water collection basin 21D has a first bottom tank panel 211D,a first side tank panel 212D, a plurality of through first passage holes213D formed in the bottom tank panel 211D, wherein the cooling water 1is arranged to be pumped into the first water collection basin 21D bythe pumping device 10 and reach the first cooling unit 24D through thefirst passage holes 213D.

On the other hand, the second water collection basin 22D has a secondbottom tank panel 221D, a second side tank panel 222D, a plurality ofthrough second passage holes 223D formed on the second bottom tank panel221D, wherein the cooling water 1 dripping from the first fill materialunit 245D in the manner as mentioned above is arranged to be collectedat the second water collection basin 22D and reaches the second coolingunit 25D through the second passage holes 223D.

FIG. 27 illustrates the flow path of the refrigerant 3. The firstcooling unit 24D further comprises a first refrigerant inlet pipe 248Dconnected to the compressor 40 (as shown in FIG. 8), and a firstrefrigerant transmission pipe 249D, wherein the corresponding heatexchanging pipes (the first through fourth heat exchanging pipes 241D,242D, 243D, 244D) are extended between the first refrigerant inlet pipe248D and the first refrigerant transmission pipe 249D.

Similarly, the second cooling unit 25D further comprises a secondrefrigerant inlet pipe 258D connected to the compressor 40, and a secondrefrigerant transmission pipe 259D, wherein the corresponding heatexchanging pipes (the fifth through eighth heat exchanging pipe 251 C,252C, 253C, 254C) are extended between the second refrigerant inlet pipe258D and the second refrigerant transmission pipe 259D.

As shown in FIG. 27 of the drawings, the first refrigerant inlet pipe248D comprises a blocking member 2481D mounted therein at a positionbetween the second heat exchanging pipe 242D and the third heatexchanging pipe 243D for guiding the refrigerant 3 sequentially flowingin the path described below.

The refrigerant 3 entering the first cooling unit 24D first enters thefirst refrigerant inlet pipe 248D and hits the blocking member 2481Dprovided therein (please referring to the right side of FIG. 27).

The refrigerant 3 hitting the blocking member 2481D is guided to flowinto the first heat exchanging pipe 241D and the second heat exchangingpipe 242D, and reaches the first refrigerant transmission pipe 249D. Therefrigerant 3 reaching the first refrigerant transmission pipe 249D isarranged to be mixed and guided to flow into the third heat exchangingpipe 243D and the fourth heat exchanging pipe 244D and flow back to thefirst refrigerant inlet pipe 248D, which is then guided to leave thefirst cooling unit 24D.

The second refrigerant inlet pipe 258D comprises a blocking member 2581Dmounted therein at a position between the sixth heat exchanging pipe252D and the seventh heat exchanging pipe 253D for guiding therefrigerant 3 sequentially flowing in the path described below (pleasereferring to the left side of FIG. 27).

The refrigerant 3 entering the second cooling unit 25D first enters thesecond refrigerant inlet pipe 258D and hits the blocking member 2581Dprovided therein. The refrigerant 3 hitting the blocking member 2581D isguided to flow into the fifth heat exchanging pipe 251D and the sixthheat exchanging pipe 252D and reaches the first refrigerant transmissionpipe 259D. The refrigerant 3 reaching the second refrigeranttransmission pipe 259D is arranged to be guided to flow into the seventhheat exchanging pipe 253D and the eighth heat exchanging pipe 254D andflow back to the second refrigerant inlet pipe 258D, which is thenguided to leave the second cooling unit 25D.

FIG. 28A to FIG. 28C illustrate another flow path of the refrigerant 3.It is important to mention that there exist many flow paths of therefrigerant 3 circulating in the multiple effect evaporative condenser.These are obvious alternatives to the present invention is varying flowpaths should also be covered by the scope of the present invention.

Moreover, for the above mentioned multiple effect evaporativecondensers, (the preferred embodiment and all of the alternativesthereof) each of the heat exchanging pipes is specifically designed andconstructed in a manner described above for achieving the maximum amountof heat transfer efficiency. A preferred embodiment of the heatexchanging pipe will first be discussed and the alternatives are thenelaborated.

Referring to FIG. 29 to FIG. 33 of the drawings, a high efficiency heatexchanging pipe 240 according to a preferred embodiment of the presentinvention is illustrated, in which the heat exchanging pipe 240comprises a pipe body 51, a plurality of inner heat exchanging fins 52,and a plurality of outer heat exchanging fins 53. (Please note that thedotted lines in FIGS. 32 and 33 illustrate the inner and outer heatexchanging fins 52, 53 extending continuously around the pipe body 51).

The inner heat exchanging fins 52 are spacedly and protrudedly extendedalong an inner surface 511 of the pipe body 51 in a spiral manner forenhancing heat exchange surface area of the corresponding heatexchanging pipe 240, and for guiding a fluid flow on the inner surface511 of the corresponding heat exchange pipe 240 along the spiral path ofthe inner heat exchanging fins 52.

The outer heat exchanging fins 53 are spacedly and protrudedly extendedalong an outer surface 512 of the pipe body 51 for enhancing heatexchange surface area of the corresponding heat exchanging pipe 240 andfor guiding a fluid flow on the outer surface 512 of the correspondingheat exchange pipe 240 along the outer heat exchanging fins 53.

It is important to mention that each of the inner heat exchanging fins52 and the outer heat exchanging fins 53 can be embodied as having awide variety of cross sectional shapes so as to optimally enhance a heatexchange surface area of the corresponding heat exchanging pipe 240. Forexample, the cross sectional shape of each of the inner heat exchangingfins 52 and the outer heat exchanging fins 53 can be embodied as “I”shape, “L” shape, “T” shape, “V” shape, “W” shape, or even “Z” shape.The different cross sectional shapes of the inner heat exchanging fins52 and the outer heat exchanging fins 53 are further illustrated in FIG.34A to FIG. 34I.

More specifically, FIG. 34A illustrates that each of the inner heatexchanging fins 52 and the outer heat exchanging fins 53 has a “V” crosssectional shape. FIG. 34B illustrates that each of the inner heatexchanging fins 52 and the outer heat exchanging fins 53 has an “S”cross sectional shape. FIG. 34D illustrates that each of the inner heatexchanging fins 52 and the outer heat exchanging fins 53 has a “Z” crosssectional shape. FIG. 34C and FIG. 34E illustrate that each of the innerheat exchanging fins 52 and the outer heat exchanging fins 53 areextended from the corresponding pipe body 51 while an outer end portionof each of these inner heat exchanging fins 52 and the outer heatexchanging fins 53 has a gradually reducing thickness so as toconstitute a sharp outer end portion. FIG. 34F illustrates that each ofthe inner heat exchanging fins 52 and the outer heat exchanging fins 53has a “w” cross sectional shape. FIG. 34G illustrates that each of theinner heat exchanging fins 52 and the outer heat exchanging fins 53 hasa wavy cross sectional shape. FIG. 34H illustrates that each of theinner heat exchanging fins 52 and the outer heat exchanging fins 53 hasa “V” cross sectional shape with very small angle of inclination. FIG.34I illustrates that each of the inner heat exchanging fins 52 and theouter heat exchanging fins 53 has a “T” cross sectional shape.

The performance of heat exchange for a particular heat exchanging pipe240 is determined by the heat flux density of that heat exchanging pipe240. The law of heat conduction, generally known as the Fourier's law,states that the time rate of heat transfer through a material isproportional to the negative gradient in the temperature and to thearea, at right angles to that gradient, through which the heat isflowing. Thus, in order to maximize the time rate of heat transfer, onehas to maximize the area for the corresponding heat exchange process.The different shapes of the inner heat exchanging fins 52 and the outerheat exchanging fins 53 are used for maximizing the surface area throughwhich heat transfer takes place.

Moreover, in order to facilitate easy cleaning of the heat exchangingpipes 240, each of the inner heat exchanging fins 52 and the outer heatexchanging fins 53 are coated with a chemical layer such as a Telfonlayer (PTFE) so as to facilitate easy detachment of dirt from the innerand outer heat exchanging fins 52, 53.

Referring to FIG. 35A, FIG. 35B, and FIG. 36 of the drawings, each ofthe heat exchanging pipes 240 can be used in conjunction with an outerprotective pipe 54. Thus, each of the heat exchanging pipes 240 furthercomprises an outer protective pipe 54 having a diameter such that thepipe body 51 and the outer heat exchange fins 53 can be inserted intothe outer protective pipe 54. More specifically, the outer protectivepipe 54 comprises a pipe member 541 and a plurality of the outer heatexchanging fins 53 outwardly extended from an outer surface 5412 of thepipe member 541 for performing heat exchange with the fluid flowingalong an exterior of the outer protective pipe 54. (Please note that thedotted lines in FIGS. 35A and 35B illustrate the inner and outer heatexchanging fins 52, 53 extending continuously around the pipe body 51.)

Moreover, as shown in FIG. 36 of the drawings, the pipe body 51 of theheat exchanging pipe 240 is arranged to completely insert into the outerprotective pipe 54, wherein fluid is allowed to flow through the pipebody 51. It is worth mentioning that the features of the outer heatexchanging fins 53 extending from the pipe member 541 are identical tothat described above. In other words, they can also be embodied ashaving a wide variety of cross sectional shapes.

It is worth mentioning that at room temperature, an inner diameter ofthe outer protective pipe 54 is actually slightly smaller than an outeror radial diameter of the outer heat exchanging fins 53 of the pipe body51, so that the pipe body 51 and the outer heat exchanging fins 53 arenot capable of receiving in the outer protective pipe 54. When amanufacturer wishes to insert the pipe body 51 into the outer protectivepipe 54, the manufacturer needs to heat up the outer protective pipe 54to an elevated temperature, and the outer protective pipe 54 will expandaccordingly. After the expansion, the manufacture is able to insert thepipe body 51 along with all the inner heat exchanging fins 52 and theouter heat exchanging fins 53 into the outer protective pipe 54.

When fluid passes through the exterior (i.e. the outer heat exchangingfins 53) of the outer protective pipe 54, heat is transmitted to thefluid flowing in the pipe body 51 through the pipe member 541, the outerheat exchanging fins 53 of the pipe body 51, and the inner heatexchanging fins 52 of the pipe body 51. The identical heat transmissionpath is also accomplished when the fluid flowing inside the pipe body 51carries heat which is to be transmitted to the fluid flowing on theexterior of the outer protective pipe 54 (i.e. flowing across the outerheat exchanging fins 53 of the pipe member 541). The function of theouter protective pipe 54 is that when the pipe body 51 accidentallybreaks, the fluid flowing through the pipe body 51 is prevented fromdirectly mixing with the fluid through outside the heat exchanging pipe240.

Referring to FIG. 37 to FIG. 39 of the drawings, a first alternativemode of the heat exchanging pipe 240′ according to the preferredembodiment of the present invention is illustrated. In this firstalternative mode, each of the heat exchanging pipes 240′ comprises apipe body 51′, a plurality of inner heat exchanging fins 52′ spacedlyand protrudedly extended along an inner surface 511′ of the pipe body51′ in a spiral manner for enhancing heat exchange surface area of thecorresponding heat exchanging pipe 240′, and for guiding a fluid flow onthe inner surface 511′ of the corresponding heat exchange pipe 240′along the spiral path of the inner heat exchanging fins 52′. (Pleasealso note that the dotted lines in FIG. 38 illustrate the inner heatexchanging fins 52′ extending continuously around the pipe body 51′).

On the other hand, each of the heat exchanging pipes 240′ furthercomprises a plurality of outer heat exchanging fins 53′ spacedly andoutwardly extended from an outer surface 512′ of the pipe body 51′. Morespecifically, each of the outer heat exchanging fins 53′ iscircumferentially extended from the outer surface 512′ of the pipe body51′ to form a heat exchanging panel for performing heat exchange withthe corresponding fluid (such as cooling water described above) flowingalong the outer surface 512′ of the pipe body 51′.

As shown in FIG. 37 of the drawings, each of the outer heat exchangingfins 53′ further has a plurality of through guiding holes 531′ spacedlyprovided thereon for facilitating flowing of fluid (such as the coolingwater 1 described above) across the outer heat exchanging fins 53′. Thefluid, such as the cooling water 1, is capable of passing through theouter heat exchanging fins 53′ through the guiding holes 531′. Moreover,each of the outer heat exchanging fins 53′ further has a plurality ofindentions 532′ formed thereon for further maximizing the surface areafor heat exchange between the outer heat exchanging fins 53′ and thefluid flowing across the corresponding heat exchanging pipes 240′.

It is important to mention that the cross sectional shape of each of theouter heat exchanging fins 53′ can be varied so as to fit differentapplications of the heat exchanging pipes 240′. For example, each of theouter heat exchanging fins 53′ can have a square or rectangular crosssectional shape as shown in FIG. 37 to FIG. 38 of the drawings. However,as shown in FIG. 40 of the drawings, the outer heat exchanging fin 53′may have a circular cross section for performing heat exchange with thecorresponding fluid, wherein the dotted lines in FIG. 40 illustrate theinner heat exchanging fins 52′ extending continuously around the pipebody 51′).

It is important to mention that the outer heat exchanging fins 53′ maybe embodied as having a wide variety of cross sectional shapes. Forexample, each of the outer heat exchanging fins 53′ may be embodied ashaving a rectangular cross sectional shape, hexagonal cross sectionalshape, octagonal cross sectional shape, or any other cross sectionalshapes.

Moreover, the heat exchanging pipes 240 (and all the alternatives)mentioned above can be used in the above-mentioned multiple effectevaporative condenser 100 and all of its alternatives. Furthermore, theheat exchanging pipes 240 will also be used in the heat exchanger 30mentioned below.

Referring to FIG. 41 and FIG. 44 of the drawings, a heater exchanger 30according to the above preferred embodiment of the present invention isillustrated. According to the preferred embodiment, the heat exchanger30 comprises a heat exchanger housing 31, an upper water chamber 33provided on an upper portion of the heat exchanger housing 31, a lowerwater chamber 34 provided on a lower portion of the heat exchangerhousing 31, and a feedback arrangement 32.

The heat exchanger housing 31 has a water inlet 311, a water outlet 312,a refrigerant inlet 314, a refrigerant outlet 315, and a cover 313detachably provided on the heat exchanger housing 31.

The upper water chamber 33 is communicated with the water outlet 312,whereas the lower water chamber 34 is communicated with the water inlet311. The heat exchanger 30 further comprises a plurality of heatexchanging pipes 240 extended between the upper water chamber 33 and thelower water chamber 34, wherein water having a relatively lowtemperature is arranged to enter the heat exchanger 30 through the waterinlet 311 and temporarily store in the lower water chamber 34. The wateris then pumped up the heat exchanger housing 31 through the heattransfer pipes 240 and temporarily store in the upper water chamber 33and leaves the heat exchanger 30 through the water outlet 312. Thepumping is accomplished by a heat exchanger pump 300.

At the same time, the refrigerant 3 is guided to enter the heatexchanger 30 through the refrigerant inlet 314 and flow through anexterior of the heat exchanging pipes 240 (i.e. along the correspondingouter heat exchanging fins 53) for performing heat exchange with thewater flowing through the corresponding heat exchanging pipes 240.During the heat exchange process between the refrigerant 3 and thewater, heat is absorbed by the refrigerant 3 which becomes evaporated(i.e. vapor state). The vapor of the refrigerant 3 is then guided toleave the heat exchanger 30 through the refrigerant outlet 315.

The feedback arrangement 32 comprising a feedback outlet 321, a feedbackinlet 322, and a feedback pipe 323 connecting the feedback outlet 321and the feedback inlet 322, wherein incompletely evaporated refrigerant3 is arranged to be fed back to the heat exchanger 30 through thefeedback outlet 321 and the feedback inlet 322 for performing anothercycle of heat exchange so as to allow the incompletely evaporatedrefrigerant 3 to be fully evaporated before leaving the heat exchanger30 and goes back to the compressor or other components of the airconditioning system.

The heat exchanger 30 further comprises a refrigerant distributor 36provided in the upper water chamber 33 for guiding the refrigerantcoming from the refrigerant inlet 314 to flow across the heat exchangingpipes 240. More specifically, the refrigerant distributor 36 comprises amain guiding pipe 361 extended form the refrigerant inlet 314, aplurality of distributing branches 362 transversely and spacedlyextended from the main guiding pipe 361, wherein each of thedistributing branches 362 has a spraying nozzle 3621 formed at the endportion thereof.

The refrigerant distributor 36 further comprises a division member 363mounted in the heat exchanger housing 31 at a position above thespraying nozzles 3621, and a guider panel 364 transversely and spacedlymounted underneath the division member 363 to define a gas cavity 365between the division member 363 and the guider panel 364, wherein therefrigerant 3 flowing through the distributing branches 362 are sprayedin the gas cavity 365 in a quasi gaseous state (i.e. partially gaseousand partially liquid state).

It is worth mentioning that the guider panel 364 has a plurality ofthrough guider holes 3641 spacedly formed thereon, wherein the heatexchanging pipes 240 are arranged to extend between the upper waterchamber 33 and the lower water chamber 34 through the guider holes 3641.However, a diameter of each of the guiding holes 3641 is slightly largerthan an outer diameter (including the outer heat exchanging fins 53) ofthe corresponding heat exchanging pipes 240 so that refrigerant 3 in itsliquid state is able to pass through the small gap between the heatexchanging pipes 240 and the corresponding sidewalls of the guidingholes 3641 and reach the lower portion of the heat exchanger housing 31from the gas cavity 365.

As shown in FIG. 42 of the drawings, the heat exchanger 30 furthercomprises a plurality of diverting panels 35 transversely, suspendedlyand spacedly mounted in the heat exchanger housing 31 at a positionunderneath the guider panel 364, wherein each two of the adjacentdiverting panels 35 is mounted at opposite sidewalls of the heatexchanger housing 31, and a diameter of each of the diverting panels 35is smaller than that of the heat exchanging housing 31 so as form apredetermined passage space between an inner end of the diverting panels35 and the corresponding opposite sidewall of the heat exchanger housing31. These passage spaces of the diverting panels 35 constitute a passagechannel 301 for evaporated refrigerant 3 to flow from the upper portion316 of the heat exchanger housing 31 to the lower portion 317 thereof,where the refrigerant outlet 315 is located.

In other words, the side edges 352 of each two adjacent diverting panels35 are mounted to two opposite inner sidewalls of the heat exchangerhousing 31 respectively such that the evaporated refrigerant 3 isarranged to move from the top portion 316 to the bottom portion 317 ofthe heat exchanger housing 31 in a zigzag manner until the evaporatedrefrigerant 3 reaches the refrigerant outlet 315.

Note also that each of the diverting panels 35 has a plurality ofpassage holes 351 spacedly formed thereon and is aligned with theguiding holes 3641 respectively, wherein the heat exchanging pipes 240are arranged to pass through the passage holes 351.

Furthermore, a diameter of each of the passage holes 351 is slightlylarger than an outer diameter (including the outer heat exchanging fins53) of the corresponding heat exchanging pipes 240 so that refrigerant 3in its liquid state is able to pass through the small gap between theheat exchanging pipes 240 and the corresponding sidewalls of the passageholes 351 and reach the lower portion 317 of the heat exchanger housing31 along the outer heat exchanging fins 53 of the corresponding heatexchanging pipes 240.

In other words, the refrigerant 3 in the liquid state is then arrangedto form a thin film flowing through the outer heat exchanging fins 53 ofthe heat exchanging pipes 240 for heat exchange with the water flowingthrough the heat exchanging pipes 240 (i.e. the interior of the heatexchanging pipes 240), and is arranged to move from the upper portion ofthe heat exchanging pipes 240 downwardly toward the bottom portionthereof. Moreover, a vertical distance between each two diverting panels35 is gradually increasing from the upper most diverting panel 35 to thelowermost diverting panel 35.

When the refrigerant 3 moves from the upper portion of the heatexchanging pipes 240 to the lower portion thereof, it absorbs heat fromthe water and evaporated at a predetermined rate. On the other hand, theheat in the water flowing through the heat exchanging pipes 240 isextracted and temperature of the water decreases when it goes from thebottom portion of the heat exchanging pipes 240 to the upper portionthereof. By the time the refrigerant 3 reaches the lower portion of theheat exchanging pipes 240, a majority of the refrigerant 3 is evaporatedand is guided to exit the heat exchanger 30 through the refrigerantoutlet 315.

As shown in FIG. 42 of the drawings, the feedback arrangement 32 furthercomprises a residue collection chamber 324 provided at a lower portion317 of the heat exchanger housing 31 and is communicated with thefeedback outlet 321 in such a manner that un-evaporated refrigerant 3(i.e. residue refrigerant 3) is arranged to be guided and collected inthe residue collection chamber 324. The residue refrigerant 3 is thenpumped back to the feedback inlet 322 through the feedback pipe 323. Thefeedback inlet 322 is communicated with the space formed between theguider panels 364 and the top diverting panel 35 in the evaporatorhousing 31, so that the residue refrigerant 3 may join the refrigerant 3coming from the distributing branches 362 and go through the heatexchanging process one more time by passing along the heat exchangingpipes 240 again.

Referring to FIG. 45 and FIG. 46 of the drawings, a first alternativemode of the heat exchanger according to the preferred embodiment of thepresent invention is schematically illustrated. The first alternativemode of the heat exchanger 30 is similar to the preferred embodimentdescribed above except refrigerant distributor 36′.

In this third alternative mode, the refrigerant distributor 36′ guidesthe flow of the refrigerant 3 outside the heat exchanger housing 31. Therefrigerant distributor 36′ comprises the main guiding pipe 361′extended from the refrigerant inlet 314′ and the distributing branches362′ are extended from the main guiding pipe 361′ which are provided atan exterior of the heat exchanger housing 31, wherein each of thedistributing branches 362′ are directly extended to the gas cavity 365′for allowing liquid refrigerant 3 to perform heat exchange with the heatexchanging pipes 240.

Referring to FIG. 47 and FIG. 50 of the drawings, a second alternativemode of the heat exchanger according to the preferred embodiment of thepresent invention is schematically illustrated. The second alternativemode of the heat exchanger 30″ is similar to the preferred embodimentdescribed above except the heat exchanging pipe 240″.

According to the second alternative mode of the heat exchanger 30″, theheat exchanger 30″ comprises only one heat exchanging pipe 240E forfacilitating heat exchanging between the water and the refrigerant 3.More specifically, the heat exchanger 30″comprises a heat exchangerhousing 31″, an upper water chamber 33″ provided on an upper portion316″ of the heat exchanger housing 31″, a lower water chamber 34″provided on a lower portion 317″ of the heat exchanger housing 31″, anda feedback arrangement 32″.

The heat exchanger housing 31″ has a water inlet 311″, a water outlet312″, a refrigerant inlet 314″, a refrigerant outlet 315″, and a cover313″ detachably provided on the heat exchanger housing 31″.

The upper water chamber 33″ is communicated with the water outlet 312″,whereas the lower water chamber 34″ is communicated with the water inlet311″, The heat exchanging pipe 240E is extended between the upper waterchamber 33″ and the lower water chamber 34″, wherein water having arelatively low temperature is arranged to enter the heat exchanger 30″through the water inlet 311″ and temporarily store in the lower waterchamber 34″, The water is then pumped up the heat exchanger housing 31″through the heat transfer pipe 240E and temporarily store in the upperwater chamber 33″ and leaves the heat exchanger 30″ through the wateroutlet 312″, The pumping is accomplished by a heat exchanger pump 300″.

At the same time, the refrigerant 3 is guided to enter the heatexchanger 30″ through the refrigerant inlet 314″ and flow through anexterior of the heat exchanging pipe 240E (i.e. along the correspondingouter heat exchanging fins 53E) for performing heat exchange with thewater flowing through the corresponding heat exchanging pipes 240E.During the heat exchange process between the refrigerant 3 and thewater, heat is absorbed by the refrigerant 3 which becomes evaporated(i.e. vapor state), The vapor of the refrigerant 3 is then guided toleave the heat exchanger 30″ through the refrigerant outlet 315″.

The feedback arrangement 32″ comprising a feedback outlet 321″, afeedback inlet 322″, and a feedback pipe 323″ connecting the feedbackoutlet 321″ and the feedback inlet 322″, wherein incompletely evaporatedrefrigerant 3 is arranged to be fed back to the heat exchanger 30″through the feedback outlet 321″ and the feedback inlet 322″ forperforming another cycle of heat exchange so as to allow theincompletely evaporated refrigerant 3 to be fully evaporated beforeleaving the heat exchanger 30″ and goes back to the compressor or othercomponents of the air conditioning system.

The refrigerant distributor is identical to what is disclosed in thepreferred embodiment, except the refrigerant distributor is arranged todistribute the refrigerant 3 to flow from the refrigerant inlet 314″ tothe only heat exchanging pipe 240E in the heat exchanger 30″.

In this second alternative mode of the heat exchanger 30″, the heatexchanger 30″ further comprises an inner spiral guiding member 37″mounted in the heat exchanging pipe 240E, wherein an outer diameter ofthe inner spiral guiding member 37″ is slightly smaller than an innerdiameter of the heat exchanging pipe 240E so that the inner spiralguiding member 37″ does not hit the inner heat exchanging fins 52E(extended from the pipe body 51E) of the heat exchanging pipe 240E.

The inner spiral guiding member 37″ further has an inner spiral guider371″ made by flexible material and is formed along an outer edge of theinner spiral guiding member 37″ for preventing the inner spiral guidingmember 37″ from hitting the inner heat exchanging fins 52E. (Please notethat the dotted lines illustrate the inner spiral guider 371″ and theinner exchanging fins 52E continuously extending around the pipe body51E.)

It is important to mention at this stage that the inner spiral guidingmember 37″ spirally extends along a longitudinally direction of the heatexchanging housing 31″ and is arranged to be extended along a directionwhich is opposite to the spirally extending inner heat exchanging fins52E of the heat exchanging pipe 240E. In other words, when the innerheat exchanging fins 52E is extended in a clockwise direction, the innerspiral guiding member 37″ is extended in an anti-clockwise direction.When the water flows through the heat exchanging pipe 240E, the flow ofthe water is guided by the inner spiral guiding member 37″. Because thespirally extending direction of the inner spiral guiding member 37″ andthe inner heat exchanging fins 52E are opposite, water flowing throughthe inner spiral guiding member 37″ is guided to hit the inner heatexchanging fins 52E. Moreover, when the inner spiral guiding member 37″is mounted in the heat exchanging pipe 240E, the water flowing time inthe heat exchanging pipe 240E will be maximized for maximizing the heatexchange time between the water and the refrigerant 3.

On the other hand, the heat exchanger 3˜″ further comprises a pluralityof outer spiral guiding members 38″ spirally, inwardly and inclinedlyextended along an inner surface of the heat exchanger housing 31″ toform a plurality of outer spiral guiders 381″, wherein the vaporrefrigerant 3 from the refrigerant inlet 314″ is arranged to hit thespiral guiding members 38″ and flow towards the outer heat exchangingfins 52E of the heat exchanging pipe 240E. The refrigerant 3 is arrangedto perform heat exchange with the water through the outer heatexchanging fins 52E and the inner heat exchanging fins 53E. Furthermore,as shown in FIG. 50 of the drawings, a vertical distance between eachtwo adjacent outer spiral guiders 381″ is increasing with decreasingheight of the heat exchanger housing 31″.

The heat exchanger 30″ further comprises an outer guider 39″ providedalong a longitudinal direction along an inner surface of the heatexchanger housing 31″ for adjusting and guiding a flowing path of therefrigerant 3 flowing through the space between the outer heatexchanging fins 52E and the inner surface of the heat exchanging housing31″. Note that when the refrigerant 3 is guided to flow in a spiralmember by the outer heat exchanging fins 52E, a centrifugal force willbe developed and the refrigerant 3 will tend to flow toward the innersurface of the heat exchanger housing 31″. The purpose of the outerguider 39″ is to guide the refrigerant hitting thereon to flow back tothe outer heat exchanging fins 52E for prolonging the time in which therefrigerant 3 contacts with the outer heat exchanging fins 52E.

Referring to FIG. 51 and FIG. 54 of the drawings, a third alternativemode of the heat exchanger according to the preferred embodiment of thepresent invention is schematically illustrated. The third alternativemode of the heat exchanger 30A is similar to the second alternative modeof the heat exchange 30″ described above, except the heat exchanger 30Afurther comprises a detachable arrangement 39A.

In this third alternative mode, the detachable arrangement 39A isprovided on the heat exchanger housing 31 A for allowing the user toreplace the heat exchanging pipe 240E by detaching the cover 313A fromthe heat exchanger housing 31A.

More specifically, the detaching arrangement 39A comprises a firstflange 391A and a second flange 392A connecting the cover 313A to theheat exchanger housing 31A. The first flange 391A has a plurality offirst connecting holes 3911A spacedly formed thereon, wherein the firstflange 391A connects the heat exchanger housing 31A with the cover 313Athrough a plurality of connectors, such as screws, penetrating throughthe first connecting holes 3911A. On the other hand, the detachingarrangement 39A further comprises a supporting frame 393A detachablyconnecting the cover 313A and the heat exchanging pipe 240E. As shown inFIG. 53 of the drawings, the second flange 392A has a plurality ofsecond connecting holes 3921A, wherein the supporting frame 393A isconnected to the second flange 392A which is in turn connected to thefirst flange 391A through a plurality of connectors, such as screws,penetrating though the second connecting holes 3921A. Note that thesecond flange 392A has a diameter smaller than that of the first flange391A, so that the cover 313A can be able to cover the second flange 392Aand the heat exchanging pipe 240E when it is connected to the firstflange 391A. Furthermore, the detaching arrangement 39A furthercomprises a sealing member 394A secured between the second flange 392Aand the pip body 51E through a plurality of securing screws 395A mountedon the second flange 392A.

The supporting frame 393A comprises a first and a second supportermember 3931A, 3932A connected with each other in a cross manner forconnecting with the second flange 392A.

It is worth mentioning that a user of the present invention may easilyreplace or take out the heat exchanging pipe 240E from the heatexchanger 30A for cleaning. The user needs only to unscrew theconnectors connecting the cover 313A and the heat exchanger housing 31Aand detach the cover 313A from the first flange 391A. Then, the userneeds to unscrew the securing screws 395A from the second flange 392A.Afterwards, the user is able to detach the second flange 392A from thefirst flange 391A and take out the heat exchanging pipe 240E along withthe supporting frame 393A from the heat exchanger housing 31A forcleaning or replacement.

FIG. 55A to FIG. 55F of the drawings illustrate that the airconditioning system of the present invention air conditioning systemfurther comprises a cooling device 60 which uses a supplemental waterwith lower temperature to cool down the liquid refrigerant. As anexample, the cooling device 60 can be connected between the expansionvalve 50 (as shown in FIG. 8) and the multiple effective evaporativecondenser 100, wherein the cooling device 60 is arranged to furtherlower the temperature of the refrigerant 3 coming out from the multipleeffect evaporative condenser 100.

The cooling device 60 comprises a tubular housing 61 having arefrigerant entrance 611 formed at a bottom portion thereof, and arefrigerant exit 612 formed at a top portion of the tubular housing 61,wherein refrigerant 3 leaving the multiple effect evaporative condenser100 is arranged to enter the tubular housing 61 through the refrigerantentrance 611 for further cooling, while the refrigerant 3 is arranged toleave the cooling device 60 through the refrigerant exit 612.

The cooling device 60 further comprises a heat exchanging pipe 240 (asdescribed above) extended from the refrigerant entrance 611 and therefrigerant exit 612, wherein the refrigerant 3 is arranged to flowthrough the heat exchanging pipe 240 in the cooling device 60. Moreover,the tubular housing 61 further has a water entrance 613 provided at atop portion thereof, and a water exit 614 provided at a bottom portionof the tubular housing 61, wherein the supplemental water is arranged toflow into the tubular housing 61 through the water entrance 613 andperform heat exchange with the refrigerant 3 for further cooling thetemperature of the refrigerant 3. Note that the water flowing throughthis cooling device 60 is collected from the multiple effect evaporativecondenser so that when the water finishes absorbing heat from therefrigerant 3, the water is guided to flow back to the multiple effectevaporative condenser for cooling.

The cooling device 60 further comprises a plurality of water diverters63 spacedly extended from inner sidewall of the tubular housing 61 insuch a manner that each of the water diverters 63 is orientated suchthat when the water is hit therein, the water is guided to flow towardsthe opposite water diverter 63 at a next lower level while passingthrough an exterior surface of the heat exchanging pipe 240 forperforming heat exchange with the refrigerant 3 flowing through the heatexchanging pipe 240. The water entering from the water entrance 613 isthus flowed in the tubular housing 61 in a zigzag path.

The tubular housing 61 comprises a first and a second housing body 615,616 detachably attached with each other to form the tubular housing 61.As shown in FIG. 55E and FIG. 55F of the drawings, each of the first andthe second housing body 615,616 has a semi-circular cross section and isdetachably connected with each other through an engaging arrangement617.

Referring to FIG. 56 to FIG. 57 of the drawings, two heat exchangers 30(namely a first heat exchanger 30 and a second heat exchanger 30) areconnected with each other in parallel and in series for furtherenhancing the heat exchange capacity of the present invention. FIG. 56illustrates two heat exchangers 30 are put in a side-by-side manner,while FIG. 57 illustrates that the two heat exchangers 30 are put in avertical configuration in a series manner. In the latter case, waterleaving the first heat exchanger 30 (located at the bottom) is guided toflow into the second heat exchanger 30 (located at the top), wherein theheat exchange mechanism in each of these first and the second heatexchanger 30 is identical to those described above. In FIG. 57, thewater leaving the first heat exchanger 30 is guided to flow into thesecond heat exchanger 30 for further extracting heat to the refrigerant3.

One skilled in the art will understand that the embodiment of thepresent invention as shown in the drawings and described above isexemplary only and not intended to be limiting. It will thus be seenthat the objects of the present invention have been fully andeffectively accomplished. It embodiments have been shown and describedfor the purposes of illustrating the functional and structuralprinciples of the present invention and is subject to change withoutdeparture from such principles. Therefore, this invention includes allmodifications encompassed within the spirit and scope of the followingclaims.

What is claimed is:
 1. A heat exchanger for facilitating heat exchangebetween a predetermined amount of water and a predetermined amount ofrefrigerant, comprising: a heat exchanger housing having a water inlet,a water outlet, a refrigerant inlet, a refrigerant outlet, and a coverdetachably provided on said heat exchanger housing, an upper waterchamber provided on an upper portion of said heat exchanger housing, andis communicated with said water outlet; a lower water chamber providedon a lower portion of said heat exchanger housing, and is communicatedwith said water inlet; and at least one heat exchanging pipe extendedbetween said upper water chamber and said lower water chamber, whereinwater having a relatively low temperature is arranged to enter said heatexchanger through said water inlet and temporarily store in said lowerwater chamber, wherein said water is pumped up said heat exchangerhousing through said heat exchanging pipes and temporarily store in saidupper water chamber and leaves said heat exchanger through said wateroutlet, wherein said heat exchanging pipe comprises a pipe body, aplurality of inner heat exchanging fins inwardly extended from said pipebody, and a plurality of outer heat exchanging fins outwardly extendedfrom said pipe body; wherein said refrigerant is guided to enter saidheat exchanger through said refrigerant inlet and flow through anexterior of outer heat exchanging fins of said heat exchanging pipes forperforming heat exchange with said water flowing through saidcorresponding inner heat exchanging fins of said heat exchanging pipes,wherein heat is absorbed by said refrigerant which becomes evaporated,wherein vapor of said refrigerant is then guided to leave said heatexchanger through said refrigerant outlet.
 2. The heat exchanger, asrecited in claim 1, further comprising a feedback arrangement comprisinga feedback outlet, a feedback inlet, and a feedback pipe connecting saidfeedback outlet and said feedback inlet, wherein incompletely evaporatedrefrigerant is arranged to be fed back to said heat exchanger throughsaid feedback outlet and said feedback inlet for performing anothercycle of heat exchange so as to allow said incompletely evaporatedrefrigerant to be fully evaporated before leaving said heat exchangerand goes back to said compressor or other components of said airconditioning system.
 3. The heat exchanger, as recited in claim 2,further comprising a plurality of heat exchanging pipe and a refrigerantdistributor provided in said upper water chamber for guiding saidrefrigerant coming from said refrigerant inlet to flow across said heatexchanging pipes, wherein said refrigerant distributor comprises a mainguiding pipe extended form said refrigerant inlet, a plurality ofdistributing branches transversely and spacedly extended from said mainguiding pipe, wherein each of said distributing branches has a sprayingnozzle formed at said end portion thereof.
 4. The heat exchanger, asrecited in claim 3, wherein said refrigerant distributor furthercomprises a division member mounted in said heat exchanger housing at aposition above said spraying nozzles, and a guider panel transverselyand spacedly mounted underneath said division member to define a gascavity between said division member and said guider panel, wherein saidrefrigerant flowing through said distributing branches are sprayed insaid gas cavity in a quasi gaseous state.
 5. The heat exchanger, asrecited in claim 4, wherein said guider panel has a plurality of throughguider holes spacedly formed thereon, wherein said heat exchanging pipesare arranged to extend between said upper water chamber and said lowerwater chamber through said guider holes, wherein a diameter of each ofsaid guiding holes is slightly larger than an outer diameter of saidcorresponding heat exchanging pipes so that said refrigerant in liquidstate is able to pass through said small gap between said heatexchanging pipes and corresponding sidewalls of said guiding holes andreach said lower portion of said heat exchanger housing from said gascavity.
 6. The heat exchanger, as recited in claim 5, further comprisinga plurality of diverting panels transversely, suspendedly and spacedlymounted in said heat exchanger housing at a position underneath saidguider panel, wherein each two of said adjacent diverting panels ismounted at opposite sidewalls of said heat exchanger housing, and adiameter of each of said diverting panels is smaller than that of saidheat exchanging housing so as form a predetermined passage space betweenan inner end of said diverting panels and said corresponding oppositesidewall of said heat exchanger housing, wherein said passage spaces ofsaid diverting panels constitute a passage channel for evaporatedrefrigerant to flow from an upper portion of said heat exchanger housingto a lower portion thereof.
 7. The heat exchanger, as recited in claim6, wherein each of said diverting panels has a plurality of passageholes spacedly formed thereon and is aligned with said guiding holesrespectively, wherein said heat exchanging pipes are arranged to passthrough said passage holes, wherein a diameter of each of said passageholes is slightly larger than an outer diameter of said correspondingheat exchanging pipes so that refrigerant in said liquid state is ableto pass through said small gap between said heat exchanging pipes andcorresponding sidewalls of said passage holes.
 8. The heat exchanger, asrecited in claim 7, wherein said feedback arrangement further comprisesa residue collection chamber provided at a lower portion of said heatexchanger housing and is communicated with said feedback outlet in sucha manner that un-evaporated refrigerant is arranged to be guided andcollected in said residue collection chamber.
 9. The heat exchanger, asrecited in claim 2, further comprising a plurality of heat exchangingpipe and a refrigerant distributor which comprises a main guiding pipeextended from said refrigerant inlet and a plurality of distributingbranches extended from said main guiding pipe which are provided at anexterior of said heat exchanger housing.
 10. The heat exchanger, asrecited in claim 9, wherein said refrigerant distributor furthercomprises a division member mounted in said heat exchanger housing, anda guider panel transversely and spacedly mounted underneath saiddivision member to define a gas cavity between said division member andsaid guider panel, wherein each of said distributing branches aredirectly extended to said gas cavity for allowing liquid refrigerant toperform heat exchange with said heat exchanging pipes.
 11. The heatexchanger, as recited in claim 10, wherein said guider panel has aplurality of through guider holes spacedly formed thereon, wherein saidheat exchanging pipes are arranged to extend between said upper waterchamber and said lower water chamber through said guider holes, whereina diameter of each of said guiding holes is slightly larger than anouter diameter of said corresponding heat exchanging pipes so that saidrefrigerant in liquid state is able to pass through said small gapbetween said heat exchanging pipes and corresponding sidewalls of saidguiding holes and reach said lower portion of said heat exchangerhousing from said gas cavity.
 12. The heat exchanger, as recited inclaim 11, further comprising a plurality of diverting panelstransversely, suspendedly and spacedly mounted in said heat exchangerhousing at a position underneath said guider panel, wherein each two ofsaid adjacent diverting panels is mounted at opposite sidewalls of saidheat exchanger housing, and a diameter of each of said diverting panelsis smaller than that of said heat exchanging housing so as form apredetermined passage space between an inner end of said divertingpanels and said corresponding opposite sidewall of said heat exchangerhousing, wherein said passage spaces of said diverting panels constitutea passage channel for evaporated refrigerant to flow from an upperportion of said heat exchanger housing to a lower portion thereof. 13.The heat exchanger, as recited in claim 12, wherein each of saiddiverting panels has a plurality of passage holes spacedly formedthereon and is aligned with said guiding holes respectively, whereinsaid heat exchanging pipes are arranged to pass through said passageholes, wherein a diameter of each of said passage holes is slightlylarger than an outer diameter of said corresponding heat exchangingpipes so that refrigerant in said liquid state is able to pass throughsaid small gap between said heat exchanging pipes and correspondingsidewalls of said passage holes.
 14. The heat exchanger, as recited inclaim 13, wherein said feedback arrangement further comprises a residuecollection chamber provided at a lower portion of said heat exchangerhousing and is communicated with said feedback outlet in such a mannerthat un-evaporated refrigerant is arranged to be guided and collected insaid residue collection chamber.
 15. The heat exchanger, as recited inclaim 14, wherein each of said heat exchanging pipes comprises a pipebody, a plurality of inner heat exchanging fins spacedly and protrudedlyextended along an inner surface of said pipe body in a spiral manner forenhancing heat exchange surface area of said corresponding heatexchanging pipe, and for guiding a fluid flow on said inner surface ofsaid corresponding heat exchange pipe along said spiral path of saidinner heat exchanging fins, and a plurality of outer heat exchangingfins spacedly and protrudedly extended along an outer surface of saidpipe body for enhancing heat exchange surface area of said correspondingheat exchanging pipe and for guiding a fluid flow on said outer surfaceof said corresponding heat exchange pipe along said outer heatexchanging fins.
 16. The heat exchanger, as recited in claim 2, furthercomprising an inner spiral guiding member mounted in said heatexchanging pipe, wherein an outer diameter of said inner spiral guidingmember is slightly smaller than an inner diameter of said heatexchanging pipe so that said inner spiral guiding member is preventedfrom hitting said heat exchanging pipe.
 17. The heat exchanger, asrecited in claim 16, wherein said inner spiral guiding member furtherhas an inner spiral guider formed along an outer edge of said innerspiral guiding member for preventing said inner spiral guiding memberfrom hitting said heat exchanging pipe.
 18. The heat exchanger, asrecited in claim 17, wherein said heat exchanging pipe comprises a pipebody, a plurality of inner heat exchanging fins spacedly and protrudedlyextended along an inner surface of said pipe body in a spiral manner forenhancing heat exchange surface area of said corresponding heatexchanging pipe, and for guiding a fluid flow on said inner surface ofsaid corresponding heat exchange pipe along said spiral path of saidinner heat exchanging fins, and a plurality of outer heat exchangingfins spacedly and protrudedly extended along an outer surface of saidpipe body for enhancing heat exchange surface area of said correspondingheat exchanging pipe and for guiding a fluid flow on said outer surfaceof said corresponding heat exchange pipe along said outer heatexchanging fins.
 19. The heat exchanger, as recited in claim 18, whereinsaid inner spiral guiding member spirally extends along a longitudinallydirection of said heat exchanging housing and is arranged to be extendedalong a direction which is opposite to said spirally extending innerheat exchanging fins of said heat exchanging pipe.
 20. The heatexchanger, as recited in claim 18, further comprising a plurality ofouter spiral guiding members spirally, inwardly and inclinedly extendedalong an inner surface of said heat exchanger housing to form aplurality of outer spiral guiders, wherein said vapor refrigerant fromsaid refrigerant inlet is arranged to hit said spiral guiding membersand flow towards said outer heat exchanging fins of said heat exchangingpipe.
 21. The heat exchanger, as recited in claim 20, wherein a verticaldistance between each two adjacent outer spiral guiders is increasingwith decreasing height of said heat exchanger housing.
 22. The heatexchanger, as recited in claim 21, further comprising an outer guiderprovided along a longitudinal direction along an inner surface of saidheat exchanger housing for adjusting and guiding a flowing path of saidrefrigerant flowing through a space between said outer heat exchangingfins and said inner surface of said heat exchanging housing.
 23. Theheat exchanger, as recited in claim 2, further comprising cover providedon said heat exchanger housing, and a detachable arrangement whichcomprises a first flange and a second flange connecting said cover tosaid heat exchanger housing, wherein said first flange has a pluralityof first connecting holes spacedly formed thereon, wherein said firstflange connects said heat exchanger housing with said cover through aplurality of connectors penetrating through said first connecting holes.24. The heat exchanger, as recited in claim 23, wherein said detachingarrangement further comprises a supporting frame detachably connectingsaid cover and said heat exchanging pipe, wherein said second flange hasa plurality of second connecting holes, wherein said supporting frame isconnected to said second flange which is in turn connected to said firstflange through a plurality of connectors penetrating though said secondconnecting holes.
 25. The heat exchanger, as recited in claim 24,wherein said second flange has a diameter smaller than that of saidfirst flange, so that said cover is capable of covering said secondflange and said heat exchanging pipe when said cover is connected tosaid first flange.
 26. The heat exchanger, as recited in claim 25,wherein said detaching arrangement further comprises a sealing membersecured between said second flange and said heat exchanging pipe througha plurality of securing screws mounted on said second flange.
 27. Theheat exchanger, as recited in claim 26, wherein said supporting framecomprises a first and a second supporter member connected with eachother in a cross manner for connecting with said second flange.
 28. Theheat exchanger, as recited in claim 27, wherein each of said heatexchanging pipes comprises a pipe body, a plurality of inner heatexchanging fins spacedly and protrudedly extended along an inner surfaceof said pipe body in a spiral manner for enhancing heat exchange surfacearea of said corresponding heat exchanging pipe, and for guiding a fluidflow on said inner surface of said corresponding heat exchange pipealong said spiral path of said inner heat exchanging fins, and aplurality of outer heat exchanging fins spacedly and protrudedlyextended along an outer surface of said pipe body for enhancing heatexchange surface area of said corresponding heat exchanging pipe and forguiding a fluid flow on said outer surface of said corresponding heatexchange pipe along said outer heat exchanging fins.